Compressor and refrigeration cycle device using same

ABSTRACT

A compressor uses a refrigerant containing R1123 (1,1,2-trifluoroethylene) as a working fluid, and uses a polyvinyl ether oil as a compressor lubricating oil. In addition, a fixed scroll and a revolving scroll each having a spiral lap rising from an end plate, and a compression chamber which is formed by meshing the fixed scroll and the revolving scroll, are provided. In addition, a discharge hole which is provided at a center position of the end plate of the fixed scroll, and is open to a discharge chamber, a bypass hole which is provided in the end plate of the fixed scroll, and communicates with the compression chamber and the discharge chamber at a timing different from a timing at which the compression chamber communicates with the discharge hole, and a check valve which is provided in the bypass hole, and allows a flow from the compression chamber side to the discharge chamber side.

TECHNICAL FIELD

The present invention relates to a compressor which uses a working fluidcontaining R1123, and a refrigeration cycle device using the same.

BACKGROUND ART

In general, in a refrigeration cycle device, a refrigeration cyclecircuit is configured by connecting a compressor, a reversing valve (asnecessary), a heat radiator (or a condenser), a decompressor, such as acapillary tube or an expansion valve, and an evaporator to each otherwith piping. In addition, by circulating a refrigerant in the insidethereof, a cooling action or a heating action is performed.

As the refrigerant in the refrigeration cycle device, halogenatedhydrocarbons which are called fluorocarbons (fluorocarbons are definedby the standard ANSI/ASHRAE 34 and are described as ROO or ROOO, andhereinafter, simply referred to as ROO or ROOO), and which are derivedfrom methane or ethane, are known.

As a refrigerant for the above-described refrigeration cycle device,R410A is widely used. However, the global warming potential (GWP) of therefrigerant R410A is 1730 which is high, and there is a problem from aviewpoint of preventing global warming.

Here, from the viewpoint of preventing global warming, as a refrigeranthaving a low GWP, for example, R1123 (1,1,2-trifluoroethylene) and R1132(1,2-difluoroethylene) have been suggested (for example, refer to PTL 1or PTL 2).

However, the stability of R1123 (1,1,2-trifluoroethylene) and R1132(1,2-clifluoroethylene) is low compared to that of refrigerants of therelated art, such as R410A, and in a case where radicals are generated,there is a concern that the refrigerant may change into another compounddue to a disproportionation reaction. Since a disproportionationreaction is accompanied by large thermal emission, there is a concernthat the reliability of the compressor and the refrigeration cycledevice may deteriorate. Therefore, in a case where R1123 or R1132 isused in the compressor and the refrigeration cycle device, it isnecessary to suppress a disproportionation reaction.

CITATION LIST Patent Literature

PTL 1: International Publication No. 2012-157764

PTL 2: International Publication No. 2012-157765

SUMMARY OF THE INVENTION

Considering the above-described problem of the related art, for example,in a compressor which is used for an air conditioner or the like, thepresent invention specifies an aspect of a more appropriate compressorin using a working fluid containing R1123. In addition, the presentinvention provides a more appropriate refrigeration cycle device inusing a working fluid containing R1123.

According to the present invention, there is provided a compressor whichuses a refrigerant containing 1,1,2-trifluoroethylene as a workingfluid, and uses a polyvinyl ether oil as a compressor lubricating oil.In addition, a fixed scroll and a revolving scroll each having a spirallap rising from an end plate; and a compression chamber which is formedby meshing the fixed scroll and the revolving scroll, are provided.Furthermore, a discharge hole which is provided at a center position ofthe end plate of the fixed scroll, and is open to a discharge chamber;and a bypass hole which is provided in the end plate of the fixedscroll, and communicates with the compression chamber and the dischargechamber at a timing different from a timing at which the compressionchamber communicates with the discharge hole, are provided. In addition,a check valve which is provided in the bypass hole, and allows a flowfrom the compression chamber side to the discharge chamber side, isprovided.

In addition, according to the present invention, there is provided acompressor which uses a refrigerant containing 1,1,2-trifluoroethyleneas a working fluid, and uses a polyvinyl ether oil as a compressorlubricating oil. In addition, a fixed scroll and a revolving scroll eachhaving a spiral lap rising from an end plate; a compression chamberwhich is formed by engaging the fixed scroll and the revolving scroll; afirst compression chamber which is formed on an outer wall side of thelap of the revolving scroll; and a second compression chamber which isformed on an inner wall side of the lap of the revolving scroll, areprovided. In addition, a suction volume of the first compression chamberis greater than a suction volume of the second compression chamber.

According to the present invention, there is provided a refrigerationcycle device including: the above-described compressor; a condenserwhich cools a refrigerant gas that is compressed by the compressor andhas a high pressure; a throttle mechanism which reduces the pressure ofthe high-pressure refrigerant which is liquefied by the condenser; anevaporator which gasifies the refrigerant of which the pressure isreduced by the throttle mechanism; and piping which links thecompressor, the condenser, the throttle mechanism, and the evaporator toeach other.

As described above, according to the present invention, it is possibleto obtain a compressor which is more appropriate in using a workingfluid containing R1123, and a refrigeration cycle device.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a system configuration view of a refrigeration cycle devicewhich uses a compressor according to a first embodiment of the presentinvention.

FIG. 2 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R32, in a mixed working fluid of R1123 andR32 in the first embodiment of the present invention.

FIG. 3 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R32, in a mixed working fluid of R1123 andR32 in the first embodiment of the present invention.

FIG. 4 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R125, in a mixed working fluid of R1123 andR125 in the first embodiment of the present invention.

FIG. 5 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R125, in a mixed working fluid of R1123 andR125 in the first embodiment of the present invention.

FIG. 6 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), in a case where proportions ofeach of R32 and R125 is fixed to 50% by weight, and R32 and R125 aremixed with R1123 in the first embodiment of the present invention.

FIG. 7 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), in a case where proportions ofeach of R32 and R125 is fixed to 50% by weight, and R32 and R125 aremixed with R1123 in the first embodiment of the present invention.

FIG. 8 is a longitudinal sectional view of a scroll compressor accordingto the first embodiment of the present invention.

FIG. 9 is a sectional view in which main portions of a compressionmechanism portion of the scroll compressor according to the firstembodiment of the present invention are enlarged.

FIG. 10 is a plan view illustrating a configuration of a compressionchamber of the compression mechanism portion of the scroll compressoraccording to the first embodiment of the present invention.

FIG. 11 is a view illustrating comparison of pressures of thecompression chambers in each of a case of the first embodiment (a casewhere a bypass hole is provided) of the present invention and a casewhere the bypass hole is not provided (comparative example).

FIG. 12 is a plan view illustrating a configuration of the compressionchamber of the compression mechanism portion of the scroll compressoraccording to a modification example of the first embodiment of thepresent invention.

FIG. 13 is a partial sectional view illustrating a structure in thevicinity of a power supply terminal of the compressor according to thefirst embodiment of the present invention.

FIG. 14 is a view illustrating a configuration of a refrigeration cycledevice according to a second embodiment of the present invention.

FIG. 15 is a Mollier diagram illustrating an operation of therefrigeration cycle device in the second embodiment of the presentinvention.

FIG. 16 is a Mollier diagram illustrating a control operation ofModification Example 1 in the second embodiment of the presentinvention.

FIG. 17 is a Mollier diagram illustrating a control operation ofModification Example 2 of a control method of the refrigeration cycledevice in the second embodiment of the present invention.

FIG. 18 is a view illustrating a piping joint which configures a part ofpiping of the refrigeration cycle device of the second embodiment of thepresent invention.

FIG. 19 is a view illustrating a configuration of a refrigeration cycledevice according to a third embodiment of the present invention.

FIG. 20 is a view illustrating a configuration of a refrigeration cycledevice according to a fourth embodiment of the present invention.

FIG. 21 is a view illustrating an operation of the refrigeration cycledevice of the fourth embodiment of the present invention in a Mollierdiagram.

FIG. 22 is a view in which main portions of a compression mechanismportion of a scroll compressor according to a fifth embodiment of thepresent invention are enlarged.

FIG. 23 is a system configuration view of a refrigeration cycle devicewhich uses a compressor according to a sixth embodiment of the presentinvention.

FIG. 24 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R32, in a mixed working fluid of R1123 andR32 in the sixth embodiment of the present invention.

FIG. 25 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R32, in a mixed working fluid of R1123 andR32 in the sixth embodiment of the present invention.

FIG. 26 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R125, in a mixed working fluid of R1123 andR125 in the sixth embodiment of the present invention.

FIG. 27 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), at proportions of 30% byweight to 60% by weight of R125, in a mixed working fluid of R1123 andR125 in the sixth embodiment of the present invention.

FIG. 28 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), in a case where proportions ofeach of R32 and R125 is fixed to 50% by weight, and R32 and R125 aremixed with R1123 in the sixth embodiment of the present invention.

FIG. 29 is a view comparing R410A and R1123 with each other by computinga refrigeration performance in a case where a pressure and a temperaturein the refrigeration cycle, and a displacement volume of the compressorare the same, and cycle efficiency (COP), in a case where proportions ofeach of R32 and R125 is fixed to 50% by weight, and R32 and R125 aremixed with R1123 in the sixth embodiment of the present invention.

FIG. 30 is a longitudinal sectional view of a scroll compressoraccording to the sixth embodiment of the present invention.

FIG. 31 is a sectional view in which main portions of a compressionmechanism portion of the scroll compressor according to the sixthembodiment of the present invention are enlarged.

FIG. 32 is a view illustrating a state where a revolving scroll mesheswith a fixed scroll in the sixth embodiment of the present invention.

FIG. 33 is a view illustrating a pressure rise curve of a firstcompression chamber and a second compression chamber in the sixthembodiment of the present invention.

FIG. 34 is a view illustrating a state where the revolving scroll mesheswith the fixed scroll and viewed from a rear surface of the revolvingscroll, in the sixth embodiment of the present invention.

FIG. 35 is a partial sectional view illustrating a structure in thevicinity of a power supply terminal of the scroll compressor accordingto the sixth embodiment of the present invention.

FIG. 36 is a view illustrating a configuration of a refrigeration cycledevice according to a seventh embodiment of the present invention.

FIG. 37 is a Mollier diagram illustrating an operation of therefrigeration cycle device in the seventh embodiment of the presentinvention.

FIG. 38 is a Mollier diagram illustrating a control operation ofModification Example 1 in the seventh embodiment of the presentinvention.

FIG. 39 is a Mollier diagram illustrating a control operation ofModification Example 2 of a control method of the refrigeration cycledevice in the seventh embodiment of the present invention.

FIG. 40 is a view illustrating a piping joint which configures a part ofpiping of the refrigeration cycle device of the seventh embodiment ofthe present invention.

FIG. 41 is a view illustrating a configuration of a refrigeration cycledevice according to an eighth embodiment of the present invention.

FIG. 42 is a view illustrating a configuration of a refrigeration cycledevice according to a ninth embodiment of the present invention.

FIG. 43 is a view illustrating an operation of the refrigeration cycledevice of the ninth embodiment of the present invention in a Mollierdiagram.

FIG. 44 is a sectional view of a scroll compressor according to a tenthembodiment of the present invention.

DESCRIPTION OF EMBODIMENTS

Hereinafter, embodiments of the present invention will be described withreference to the drawings. In addition, the present invention is notlimited to the embodiments.

First Embodiment

First, a first embodiment of the present invention will be described.

FIG. 1 is a system configuration view of refrigeration cycle device 100which uses compressor 61 according to the first embodiment of thepresent invention.

As illustrated in FIG. 1, refrigeration cycle device 100 of theembodiment is mainly configured of compressor 61, condenser 62, throttlemechanism 63, and evaporator 64, for example, in a case of a cycleexclusively for cooling. In addition, the equipment is linked to eachother so that a working fluid (refrigerant) circulates by piping.

In refrigeration cycle device 100 configured as described above, therefrigerant changes to liquid by at least any of pressurizing andcooling, and changes to gas by at least any of pressurizing and heating.Compressor 61 is driven by a motor, and transports a low-temperature andlow-pressure gas refrigerant to condenser 62 by pressurizing the gasrefrigerant to a high-temperature and high-pressure gas refrigerant. Incondenser 62, the high-temperature and high-pressure gas refrigerant iscooled by air blown by a fan or the like, is condensed, and becomes alow-temperature and high-pressure liquid refrigerant. A pressure of theliquid refrigerant is reduced by throttle mechanism 63, a part of theliquid refrigerant becomes the low-temperature and low-pressure gasrefrigerant, a remaining part becomes a low-temperature and low-pressureliquid refrigerant, and the liquid refrigerant is transported toevaporator 64. In evaporator 64, the low-temperature and low-pressureliquid refrigerant is heated and evaporated by the air blown by the fanor the like, becomes the low-temperature and low-pressure gasrefrigerant, is suctioned to compressor 61 again, and is pressurized.The cycle is repeatedly performed.

In addition, in the description above, refrigeration cycle device 100exclusively for cooling is described, but by using reversing valve orthe like, it is certainly possible to operate refrigeration cycle device100 as a cycle device for heating.

In addition, it is desirable that a heat transfer pipe which configuresa refrigerant flow path of a heat exchanger in at least any of condenser62 and evaporator 64, is an aluminum refrigerant pipe including aluminumor aluminum alloy. In particular, it is desirable that the heat transferpipe is a flattened pipe provided with a plurality of refrigerant flowholes on a condition that a condensation temperature is lowered or anevaporation temperature is raised.

The working fluid (refrigerant, working refrigerant) which is sealed inrefrigeration cycle device 100 of the embodiment is a two-componentmixed working fluid made of (1) R1123 (1,1,2-trifluoroethylene) and (2)R32 (difluoromethane), and in particular, is a mixed working fluid inwhich there is 30% by weight to 60% by weight of R32.

In a case of employment to scroll compressor 200 which will describedlater, by mixing 30% by weight or more of R32 with R1123, it is possibleto suppress a disproportionation reaction of R1123. As a concentrationof R32 increases, it is possible to further suppress adisproportionation reaction. This is because it is possible to suppressa disproportionation reaction of R1123 by an action of reducing a chanceof a disproportionation reaction due to integrated behaviors during aphase change, such as condensation and evaporation since an action ofR32 for mitigating a disproportionation reaction by small polarizationto a fluorine atom, and physical properties of R1123 and R32 are similarto each other.

In addition, a mixed refrigerant of R1123 and R32 can be handled as asingle refrigerant since the mixed refrigerant of R1123 and R32 has anazeotropic point when R32 is 30% by weight and R1123 is 70% by weight,and a temperature does not slip. In addition, when 60% by weight or moreof R32 is mixed with R1123, the temperature slide increases, and sincethere is a possibility that it is difficult to handle the singlerefrigerant in a similar manner, it is desirable to mix 60% by weight orless of R32 with R1123. In particular, in order to preventdisproportionation, to further reduce the temperature slide whenapproaching the azeotropic point, and to easily design the equipment, itis desirable that R32 is mixed at a ratio of 40% by weight to 50% byweight with R1123.

FIGS. 2 and 3 are views comparing R410A and R1123 with each other bycomputing a refrigeration performance in a case where a pressure and atemperature in the refrigeration cycle, and a displacement volume of thecompressor are the same, and cycle efficiency (COP), at proportions of30% by weight to 60% by weight of R32, in a mixed working fluid of R1123and R32 in the first embodiment of the present invention.

First, the computation condition of FIGS. 2 and 3 will be described. Inrecent years, in order to improve the cycle efficiency of the equipment,the performance of the heat exchanger is improved, and in an actualoperation state, there is a tendency for a condensation temperature todecrease, and for an evaporation temperature to increase, and there isalso a tendency for a discharge temperature to decrease. Therefore,considering the actual operation condition, a cooling computationcondition of FIG. 2 is a condition which corresponds to the time when acooling operation of an air conditioner (an indoor dry-bulb temperatureis 27° C., a wet-bulb temperature is 19° C., and an outdoor dry-bulbtemperature is 35° C.) is performed, and the evaporation temperature is15° C., the condensation temperature is 45° C., an overheating degree ofsuctioned refrigerant of the compressor is 5° C., and an overcoolingdegree of an outlet of the condenser is 8° C.

In addition, a heating computation condition of FIG. 3 is a computationcondition which corresponds to the time when a heating operation of theair conditioner (an indoor dry-bulb temperature is 20° C., an outdoordry-bulb temperature is 7° C., and a dry-bulb temperature is 6° C.) isperformed, the evaporation temperature is 2° C., the condensationtemperature is 38° C., an overheating degree of suctioned refrigerant ofthe compressor is 2° C., and an overcooling degree of an outlet of thecondenser is 12° C.

As illustrated in FIGS. 2 and 3, by mixing R32 at a ratio of 30% byweight to 60% by weight with R1123, when performing the coolingoperation and the heating operation, comparing with R410A, it isascertained that a refrigeration performance increases approximately by20%, the cycle efficiency (COP) is 94 to 97%, and the global warmingpotential can be reduced to 10 to 20% of R410A.

As described above, in a two-component system of R1123 and R32, whencomprehensively considering prevention of disproportionation, a size oftemperature slide, a performance when the cooling operation is performedand when the heating operation is performed, and COP (that is, whenspecifying the proportions employed in the air conditioner which usesscroll compressor 200 that will be described later), a mixturecontaining R32 at a ratio of 30% by weight to 60% by weight isdesirable. More desirably, a mixture containing R32 at a ratio of 40% byweight to 50% by weight is desirable.

Modification Example 1 of Working Fluid

In addition, the working fluid sealed in refrigeration cycle device 100of the embodiment is a two-component mixed working fluid made of (1)R1123 (1,1,2-trifluoroethylene) and (2) R125 (tetrafluoroethane), and inparticular, is a mixed working fluid in which there is 30% by weight to60% by weight of R125.

In a case of employment to scroll compressor 200 which will describedlater, by mixing 30% by weight or more of R125 with R1123, it ispossible to suppress a disproportionation reaction of R1123. As aconcentration of R125 increases, it is possible to further suppress adisproportionation reaction. This is because it is possible to suppressa disproportionation reaction of R1123 by an action of reducing a chanceof a disproportionation reaction due to integrated behaviors during aphase change, such as condensation and evaporation since an action ofR125 for mitigating a disproportionation reaction by small polarizationto a fluorine atom, and physical properties of R1123 and R125 aresimilar to each other. In addition, since R125 is a nonflammablerefrigerant, R125 can reduce flammability of R1123.

FIGS. 4 and 5 are views comparing R410A and R1123 with each other bycomputing a refrigeration performance in a case where a pressure and atemperature in the refrigeration cycle, and a displacement volume of thecompressor are the same, and cycle efficiency (COP), at proportions of30% by weight to 60% by weight of R125, in a mixed working fluid ofR1123 and R125 in the first embodiment of the present invention. Inaddition, each of the computation conditions of FIGS. 4 and 5 is similarto those of FIGS. 2 and 3.

As illustrated in FIGS. 4 and 5, by mixing R125 at a ratio of 30% byweight to 60% by weight with R1123, comparing with R410A, it isascertained that a refrigeration performance increases by 96% to 110%,and the cycle efficiency (COP) is 94 to 97%.

In particular, by mixing R125 at a ratio of 40% by weight to 50% byweight with R1123, since disproportionation of R1123 can be preventedand the discharge temperature can be lowered, a design of the equipmentwhen a high-load operation is performed and when freezing andrefrigerating are performed for increasing the discharge temperaturebecomes easy. Furthermore, the global warming potential can be reducedto 50 to 100% of R410A.

As described above, in a two-component system of R1123 and R125, whencomprehensively considering prevention of disproportionation, reductionof flammability, a performance when the cooling operation is performedand when the heating operation is performed, COP, and the dischargetemperature (that is, when specifying the proportions employed in theair conditioner which uses scroll compressor 200 that will be describedlater), a mixture containing R125 at a ratio of 30% by weight to 60% byweight is desirable. More desirably, a mixture containing R125 at aratio of 40% by weight to 50% by weight is desirable.

Modification Example 2 of Working Fluid

In addition, the working fluid sealed in the refrigeration cycle deviceof the embodiment may be a three-component mixed working fluid made of(1) R1123 (1,1,2-trifluoroethylene), (2) R32 (difluoromethane), and (3)R125 (tetrafluoroethane). In particular, the working fluid is a mixedworking fluid in which the proportions of R32 and R125 is equal to orgreater than 30% and less than 60% by weight, and the proportions ofR1123 is equal to or greater than 40% by weight and less than 70% byweight.

In a case of employment to scroll compressor 200 which will describedlater, by making proportions of R32 and R125 be equal to or greater than30% by weight, it is possible to suppress a disproportionation reactionof R1123. In addition, as proportions of R32 and R125 increases, it ispossible to further suppress a disproportionation reaction. In addition,R125 can reduce flammability of R1123.

FIGS. 6 and 7 are views comparing R410A and R1123 with each other bycomputing a refrigeration performance in a case where a pressure and atemperature in the refrigeration cycle, and a displacement volume of thecompressor are the same, and cycle efficiency (COP), in a case whereproportions of each of R32 and R125 is fixed to 50% by weight, and R32and R125 are mixed with R1123 in the first embodiment of the presentinvention. In addition, calculation conditions of FIG. 6 and FIG. 7 arerespectively similar to calculation conditions of FIG. 2 and FIG. 3.

As illustrated in FIGS. 6 and 7, by making proportions of each of R32and R125 30% by weight to 60% by weight, comparing with R410A, it isascertained that a refrigeration performance becomes 107 to 116%, andthe cycle efficiency (COP) is 93 to 96%.

In particular, by making proportions of R32 and R125 40% by weight to50% by weight, disproportionation can be prevented, the dischargetemperature can be lowered, and flammability can be reduced.Furthermore, the global warming potential can be reduced to 60 to 30% ofR410A.

In addition, in <Modification Example 2 of Working Fluid>, it isdescribed that proportions of each of R32 and R125 of three-componentworking fluid is made to be 50% by weight, but proportions of R32 may be0% by weight to 100% by weight, and proportions of R32 may be raised ina case where the refrigeration performance is desired to be improved. Onthe contrary, when reducing proportions of R32 and increasingproportions of R125, the discharge temperature can be lowered, andadditionally, flammability can be reduced.

As described above, in a three-component system of R1123, R32, and R125,when comprehensively considering prevention of disproportionation,reduction of flammability, a performance when the cooling operation isperformed and when the heating operation is performed, COP, and thedischarge temperature (that is, when specifying the proportions employedin the air conditioner which uses scroll compressor 200 that will bedescribed later), a mixture in which R32 and R125 are mixed and a sum ofR32 and R125 is 30% by weight to 60% by weight is desirable. Moredesirably, a mixture in which a sum of R32 and R125 is 40% by weight to50% by weight is desirable.

Next, a configuration of scroll compressor 200 which is an example ofcompressor 61 according to the embodiment will be described.

FIG. 8 is a longitudinal sectional view of scroll compressor 200according to the first embodiment of the present invention, FIG. 9 is asectional view in which main portions of compression mechanism portion 2of the same scroll compressor 200, and FIG. 10 is a plan viewillustrating a configuration of compression chamber 15 of compressionmechanism portion 2 of the same scroll compressor 200. Hereinafter, theconfiguration, the operation, and the action of scroll compressor 200will be described.

As illustrated in FIG. 8, scroll compressor 200 of the first embodimentof the present invention includes airtight container 1, compressionmechanism portion 2 in the inside thereof, motor portion 3, and oilstorage portion 20.

By using FIG. 9, compression mechanism portion 2 will be described indetail. Compression mechanism portion 2 includes main bearing member 11which is fixed to the inside of airtight container 1 by welding orshrink-fitting, shaft 4 which is pivotally supported by main bearingmember 11, and fixed scroll 12 which is bolted on main bearing member11. Compression mechanism portion 2 is configured as revolving scroll 13which meshes with fixed scroll 12 is interposed between main bearingmember 11 and fixed scroll 12.

Between revolving scroll 13 and main bearing member 11, rotationrestraining mechanism 14 using an Oldham ring or the like, which guidesrevolving scroll 13 to be operated following a circular orbit bypreventing rotation of revolving scroll 13, is provided. It is possibleto operate revolving scroll 13 following a circular orbit byeccentrically driving revolving scroll 13 using eccentric shaft portion4 a which is at an upper end of shaft 4. In addition, fixed scroll 12and revolving scroll 13 respectively have a structure in which a spirallap rises (protrudes) from an end plate.

Accordingly, compression chamber 15 which is formed between fixed scroll12 and revolving scroll 13 performs compression after suctioning andconfining a working refrigerant in compression chamber 15 via suctionpipe 16 which passes through the outside of airtight container 1 andsuction port 17 of an outer circumferential portion of fixed scroll 12by moving the working refrigerant toward a center portion from an outercircumferential side while contracting an interval volume. The workingrefrigerant of which a pressure reaches a predetermined pressure isdischarged to discharge chamber 31 by pushing and opening discharge hole18 which is a through hole formed at the center portion (end platecenter portion) of fixed scroll 12, and reed valve 19 (check valve)which is formed at a position different from that of discharge hole 18on the end plate of fixed scroll 12 and is from circular bypass hole 68which is a through hole.

Discharge chamber 31 is a space which is provided to cover dischargehole 18, and is formed by muffler 32. The working refrigerant dischargedto discharge chamber 31 is discharged to the inside of airtightcontainer 1 via a communication path provided in compression mechanismportion 2. Working refrigerant discharged to the inside of airtightcontainer 1 is discharged to refrigeration cycle device 100 fromairtight container 1 via discharge pipe 50.

In addition, in order to avoid damage due to excessive deformation ofreed valve 19, valve stop 69 which suppresses a lift amount is provided.In addition, reed valve 19 is provided, for example, on an end platesurface at a position at which bypass hole 68 of the end plate of fixedscroll 12 is formed.

In addition, as illustrated in FIG. 8, pump 25 is provided at the otherend of shaft 4, and a suction port of pump 25 is disposed to be presentin the inside of oil storage portion 20. Since pump 25 is driventogether with scroll compressor 200 at the same time, and compressorlubricating oil 6 (oil, refrigerator oil) which is in oil storageportion 20 provided on a bottom portion of airtight container 1 can bereliably suctioned up regardless of a pressure condition and anoperation speed, and a concern about shortage of oil is solved.

Compressor lubricating oil 6 which is suctioned up by pump 25 issupplied to compression mechanism portion 2 through oil supply hole 26(refer to FIG. 9) which penetrates the inside of shaft 4. In addition,before compressor lubricating oil 6 is suctioned up by pump 25, or aftercompressor lubricating oil 6 is suctioned up, by removing foreignmaterials by an oil filter or the like, it is possible to prevent theforeign materials from being incorporated into compression mechanismportion 2, and further, to improve the reliability.

Compressor lubricating oil 6 guided to compression mechanism portion 2also becomes a backpressure source with respect to revolving scroll 13,which has a pressure having substantially equivalent to a dischargepressure of scroll compressor 200. Accordingly, revolving scroll 13stably achieves a predetermined compression performance without beingseparated from or abuts against fixed scroll 12 being biased.Furthermore, by a supply pressure and a self-weight, a part ofcompressor lubricating oil 6 infiltrates into a fitting portion betweeneccentric shaft portion 4 a and revolving scroll 13, and into bearingportion 66 between shaft 4 and main bearing member 11, by obtaining ameans of escape, and after each part is lubricated, the part ofcompressor lubricating oil 6 is dropped and returns to oil storageportion 20.

In addition, by disposing seal member 78 on rear surface 13 e of the endplate of revolving scroll 13, an inner side of seal member 78 is definedas high-pressure region 30, and an outer side of seal member 78 isdefined as backpressure chamber 29. In this manner, since it is possibleto completely separate a pressure of high-pressure region 30 and apressure of backpressure chamber 29 from each other, it is possible tostably control a pressure load from rear surface 13 e of revolvingscroll 13.

Next, by using FIG. 10, a pressure rise of compression chamber 15 whichis formed by fixed scroll 12 and revolving scroll 13 will be described.In compression chamber 15 which is formed by fixed scroll 12 andrevolving scroll 13, first compression chambers 15 a-1 and 15 a-2 whichare formed on a lap outer wall side of revolving scroll 13, and secondcompression chambers 15 b-1 and 15 b-2 which are formed on a lap innerwall side, are present (this configuration in which the compressionchambers are formed on each of the outer wall side and the inner wallside of the lap, is described as “a configuration in which thecompression chambers are formed in both directions). Gas which issuctioned to each of compression chambers 15 moves to the center whilecontracting an interval volume according to a revolving operation ofrevolving scroll 13. In addition, when a pressure of the inside ofcompression chamber 15 reaches the discharge pressure, and the inside ofcompression chamber 15 communicates with discharge hole 18 or bypassholes 68 a-1, 68 a-2, 68 b-1, and 68 b-2, the working refrigerant ofcompression chamber 15 is discharged to discharge chamber 31 by pushingand opening reed valve 19. At this time, comparison of pressures ofcompression chambers 15 in each of a case where bypass holes 68 a-1, 68a-2, 68 b-1, and 68 b-2 are provided (the embodiment) and a case wherebypass holes 68 a-1, 68 a-2, 68 b-1, and 68 b-2 are not provided(comparative example), will be described.

FIG. 11 is a view illustrating comparison of pressures of compressionchambers 15 in each of a case of the first embodiment (a case wherebypass holes 68 a-1, 68 a-2, 68 b-1, and 68 b-2 are provided) of thepresent invention and a case where bypass holes 68 a-1, 68 a-2, 68 b-1,and 68 b-2 are not provided (comparative example).

As illustrated in FIG. 11, in a case where bypass holes 68 a-1, 68 a-2,68 b-1, and 68 b-2 are not provided (both in a case illustrated by asolid line and in a case illustrated by a broken line), the pressure ofcompression chamber 15 continues to increase until compression chamber15 communicates with discharge hole 18. Therefore, there is apossibility that the pressure excessively increases to be higher thanthe discharge pressure of discharge chamber 31, and the dischargetemperature increases more than necessary.

Here, in the embodiment, bypass holes 68 a-1, 68 a-2, 68 b-1, and 68 b-2are disposed at a position of communicating with compression chamber 15earlier (at an early timing) than discharge hole 18. Accordingly, at thesame time when the pressure of compression chamber 15 reaches thedischarge pressure, the discharge to discharge chamber 31 is startedthrough bypass holes 68 a-1, 68 a-2, 68 b-1, and 68 b-2, and aconfiguration which can suppress a discharge temperature rise due to theexcessive pressure rise, can be realized.

In addition, by considering bypass holes 68 a-1, 68 a-2, 68 b-1, and 68b-2 as a circular communication hole, it is possible to configure flowpath resistance with respect to areas of bypass holes 68 a-1, 68 a-2, 68b-1, and 68 b-2 to be the minimum resistance compared that in a case ofother shapes. Furthermore, as illustrated in FIG. 11, in each of thefirst compression chambers 15 a-1 and 15 a-2 (solid line) and the secondcompression chambers 15 b-1 and 15 b-2 (broken line), a crank rotationangle which reaches a discharge pressure varies. Accordingly, in theembodiment, bypass holes 68 a-1 and 68 a-2 are provided at anappropriate position of communicating only with first compressionchambers 15 a-1 and 15 a-2, and bypass holes 68 b-1 and 68 b-2 areprovided at an appropriate position of communicating only with thesecond compression chambers 15 b-1 and 15 b-2. Accordingly, immediatelybefore ejection from discharge hole 18, since it is possible to suppressa temperature rise due to the excessive compression of the refrigerant,it is possible to suppress a disproportionation reaction of R1123.

Next, a modification example of the above-described scroll compressor200 will be described.

FIG. 12 is a plan view illustrating a configuration of compressionchamber 15 of compression mechanism portion 2 of scroll compressor 200according to a modification example of the first embodiment of thepresent invention.

Since configuration elements other than bypass hole 68 ab are similar tothose described in FIG. 10, in FIG. 12, the configuration elements whichare the same as those in FIG. 10 use the same reference numerals, andonly bypass hole 68 ab will be described, and description of otherconfiguration elements is omitted.

In scroll compressor 200 illustrated in FIG. 12, by the revolvingoperation of revolving scroll 13, bypass hole 68 ab is provided at aposition which communicates with both of a first compression chamber 15a and a second compression chamber 15 b by a revolving movement ofrevolving scroll 13. In addition, at the same time, a diameter of bypasshole 68 ab is configured to be smaller than a thickness of a revolvingscroll lap 13 c not to be open to the first compression chamber 15 a andthe second compression chamber 15 b. Accordingly, in the crank rotationangle in FIG. 12, respectively, bypass hole 68 ab-1 communicates withthe second compression chamber 15 b-1, and bypass hole 68 ab-3communicates with first compression chamber 15 a-1, and bypass hole 68ab-1 and bypass hole 68 ab-3 play a role of preventing excessivecompression communicating with each other. In addition, by making such adiameter, similar to bypass hole 68 ab-2 of FIG. 12, when the revolvingscroll lap 13 c is across bypass hole 68 ab, bypass hole 68 ab does notcommunicate with either the first compression chamber 15 a-1 and thesecond compression chamber 15 b-1. Accordingly, since workingrefrigerant leakage does not occur between the compression chambers, andthe temperature rise can be suppressed, it is possible to suppress adisproportionation reaction of R1123.

In addition, in the compressor of the embodiment, as the compressorlubricating oil, polyvinyl ether oil is used.

In addition, as an additive which is added to compressor lubricating oil6, it is possible to use an additive containing at least one type of aphosphate ester anti-wear agent and a phenolic antioxidant.

Specific examples of the phosphate ester anti-wear agent includetributylphosphate, tripentyl phosphate, trihexyl phosphate, triheptylphosphate, trioctyl phosphate, trinonyl phosphate, tridecyl phosphate,tridecylic phosphate, triundodecyl phosphate, tridodecyl phosphate,tritridecyl phosphate, tritetradecyl phosphate, tripentadecyl phosphate,trihexadecyl phosphate, triheptadecyl phosphate, trioctadecyl phosphate,trioleyl phosphate, triphenyl phosphate, tricresyl phosphate, trixylenylphosphate, cresyl diphenyl phosphate, and diphenyl xylenyl phosphate. Ingeneral, by adding 0.1 to 3 wt % of the phosphate ester anti-wear agentinto the refrigerator oil, by effectively adsorbing the phosphate esteranti-wear agent to a front surface of a sliding portion, and by creatinga film having a small shearing force on a sliding surface, it ispossible to obtain an anti-wear effect.

According to this configuration, by a sliding improving effect caused bythe anti-wear agent, it is possible to suppress local heat generation ofthe sliding portion, and to obtain an effect of suppressingself-degradable reaction of the refrigerant R1123.

In addition, specific examples of the phenolic antioxidant includepropyl gallate, 2,4,5-trihydroxybutyrophenone, t-butylhydroquinone,nordihydroguaiaretic acid, butyl hydroxyanisole, 4-hydroxymethyl-2,6-di-t-butylphenol, octyl gallate, butylhydroxytoluene, and dodecylgallate. By adding 0.1 to 1 wt % of antioxidant to base oil, it ispossible to effectively captures the radicals, and to prevent thereaction. In addition, minimize coloring of the base oil itself due tothe antioxidant.

According to this configuration, as the phenolic antioxidant effectivelycaptures the radicals generated in the inside of airtight container 1,it is possible to obtain an effect of suppressing a disproportionationreaction of R1123.

In addition, limonene may be added in an amount of approximately 5% ofthe refrigerant amount of R1123 in order to prevent the reaction ofhighly reactive molecules containing a double bond and fluorine atomlike R1123. Scroll compressor 200 of the embodiment and refrigerationcycle device 100 which uses the same have a closed system, and asdescribed above, the lubricating oil is sealed as the base oil. Ingeneral, the viscosity of the lubricating oil which becomes the base oilsealed in scroll compressor 200 is generally approximately 32 mm²/s to68 mm²/s. Meanwhile, the viscosity of limonene is very low which isapproximately 0.8 mm²/s. Therefore, the viscosity of the lubricating oilrapidly decreases to be 60 mm²/s in a case where approximately 5% oflimonene is mixed therein, 48 mm²/s in a case where 15% of limonene ismixed therein, and 32 mm²/s in a case where 35% of limonene is mixedtherein. Therefore, in order to prevent the reaction of R1123, when alarge amount of limonene is mixed therein, the reliability of scrollcompressor 200 and refrigeration cycle device 100 is influenced by thedecrease in viscosity of the lubricating oil, for example, wear due to alubricating defect and generation of metallic soap due to a contactstate of metal on the sliding surface.

Meanwhile, in order to compensate for the decrease in viscosity of thebase oil generated by mixing limonene having an amount appropriate forpreventing the reaction therein, by employing high-viscosity lubricatingoil as a base, or by mixing super-high-viscosity lubricating oil havingan amount which is equal to or greater than a mixing amount of limonene,the lubricating oil of scroll compressor 200 of the embodiment ensuresappropriate viscosity of the lubricating oil.

Specifically, when lubricating oil of which the viscosity is 78 mm²/s ina case where 5% of limonene is mixed therein, and lubricating oil ofwhich the viscosity is approximately 230 mm²/s in a case where 35% oflimonene is mixed therein, are selected, it is possible to ensure 68mm²/s in viscosity after the mixing. In addition, in order to maximizean effect of preventing the reaction of R1123 using limonene, an extremeexample, such as increase in the mixing amount of limonene to 70% or80%, is also considered. However, in this case, the viscosity of thehigh-viscosity lubricating oil which becomes the base becomes 8500 mm²/sor 25000 mm²/s, respectively, and exceeds 3200 mm²/s that is the maximumvalue of ISO standard. In addition, since it is also difficult touniform mix limonene therein, actual employment is difficult to beconsidered.

In addition, in a case where super-high viscosity lubricating oil ismixed with limonene by an amount equivalent to each other, by mixing 800mm²/s to 1000 mm²/s of lubricating oil with limonene, viscosity of 32mm²/s to 68 mm²/s is obtained. In addition, in a case where the limoneneand the super-high viscosity oil which have different viscosity aremixed with each other, when performing the mixing while adding thesuper-high viscosity oil to the limonene little by little, lubricatingoil of which composition viscosity is relatively uniform, can beobtained.

In addition, limonene is described as an example in the embodiment, butsimilar effects can also be obtained by a terpene type or a terpenoidtype. For example, it is possible to select hemiterpene type isoprene,prenol, 3-methyl butanoic acid and monoterpene type geranyl diphosphatecineole, farnesyl diphosphates of pinene and sesquiterpene, artemisinin,bisabolol, diterpene type geranylgeranyl diphosphate, retinol, retinal,phytol, paclitaxel, forskolin, aphidicolin and triterpene type squalene,and lanosterol, in accordance with a use temperature of scrollcompressor 200 and refrigeration cycle device 100, and requiredviscosity of the lubricating oil.

In addition, the exemplified viscosity is a specific example in scrollcompressor 200 having a high-pressure container, but in scrollcompressor 200 which uses the lubricating oil having comparatively lowviscosity of 5 mm²/s to 32 mm²/s, and has a low-pressure container,similar embodiment is also possible, and similar effects can beobtained.

In addition, the terpene type and the terpenoid type, such as limonene,has solubility with respect to plastic, but when limonene having anamount which is equal to or less than 30% is mixed therein, theinfluence thereof is small, and electric insulation required for plasticin scroll compressor 200 does not have a problem. However, in a casewhere there is a problem, for example, in a case where the reliabilityis required for a long period of time, and in a case where a general usetemperature is high, it is desirable to use polyimide, polyimidoamide,or polyphenylene sulfide which has chemical resistant properties.

In addition, a winding wire of motor portion 3 of scroll compressor 200of the embodiment, a conductor is coated with varnish (thermosettinginsulating material) and baked with an insulating film therebetween.Examples of the thermosetting insulating material include a polyimideresin, an epoxy resin, and an unsaturated polyester resin. Among these,the polyamide resin can be obtained by coating in a state of polyamicacid which is a precursor, and baking the polyamic acid approximately at300° C. to achieve polyimidation. It is known that imide reaction occursdue to reaction between amine and carboxylic acid anhydride. Since thereis a possibility that the refrigerant R1123 also reacts in a shortcircuit between electrodes, by coating a motor winding with polyimidicacid varnish (polyimide precursor which can allow aromatic diamine andaromatic tetracarboxylic dianhydride to react is a main component), itis possible to prevent a short circuit between electrodes.

Therefore, even in a state where a coil of motor portion 3 infiltratesinto a liquid refrigerant, it is possible to maintain high resistancebetween windings, to suppress discharge between windings, and to obtainan effect of suppressing self-degradable reaction of the refrigerantR1123.

FIG. 13 is a partial sectional view illustrating a structure in thevicinity of a power supply terminal of scroll compressor 200 accordingto the first embodiment of the present invention.

In FIG. 13, power supply terminal 71, glass insulating material 72,metal lid body 73 which holds the power supply terminal, flag terminal74 which is connected to power supply terminal 71, and lead wire 75, areillustrated. In scroll compressor 200 according to the embodiment, adoughnut-like insulating member 76 which adheres to glass insulatingmaterial 72 which is an insulating member, is pipe-connected onto powersupply terminal 71 on an inner side of airtight container 1 of scrollcompressor 200. As doughnut-like insulating member 76, a member whichmaintains insulation properties and has resistance against fluorinatedacid, is appropriate. For example, a ceramic insulator or a HNBR rubberdoughnut-like spacer is employed. It is mandatory that doughnut-likeinsulating member 76 adheres to glass insulating material 72, but it ispreferable doughnut-like insulating member 76 also adheres to aconnection terminal.

In power supply terminal 71 configured in this manner, due todoughnut-like insulating member 76, a creeping distance on the powersupply terminal and an inner surface of scroll compressor 200 of a lidbody becomes long, terminal tracking can be prevented, and ignitioncaused by discharge energy of R1123 can be prevented. In addition, it ispossible to prevent fluorinated acid generated by decomposing R1123 fromcorroding glass insulating material 72.

In addition, scroll compressor 200 of the embodiment may be a so-calledhigh-pressure shell type compressor in which a discharge port is open tothe inside of airtight container 1, and the inside of airtight container1 is filled with refrigerant compressed in compression chamber 15.Meanwhile, scroll compressor 200 may be a so-called low-pressure shelltype scroll compressor 200 in which suction port 17 is open to theinside of airtight container 1, and the inside of airtight container 1is filled with refrigerant which is before being pressed in compressionchamber 15. This case is desirable because the temperature substantiallydecreases due to the introduction of a low-temperature refrigerant incompression chamber 15, and a disproportionation reaction of R1123 issuppressed, in a configuration in which a temperature is likely toincrease until the refrigerant is heated in the inside of airtightcontainer 1 and is introduced to compression chamber 15.

In addition, in high-pressure shell type scroll compressor 200, afterthe refrigerant discharged from the discharge port passes through theperiphery of motor portion 3, and is heated by motor portion 3 in theinside of airtight container 1, the refrigerant may be discharged to theoutside of airtight container 1 from discharge pipe 50. Thisconfiguration is desirable because a disproportionation reaction ofR1123 is suppressed since it is possible to decrease the temperature ofthe refrigerant in compression chamber 15, even when the temperature ofthe refrigerant discharged from discharge pipe 50 is equivalent.

Second Embodiment

Next, a second embodiment of the present invention will be described.

FIG. 14 is a view illustrating a configuration of refrigeration cycledevice 101 according to the second embodiment of the present invention.

Refrigeration cycle device 101 of the embodiment is connected tocompressor 102, condenser 103, expansion valve 104 which is a throttlemechanism, and evaporator 105 in order by refrigerant piping 106, and arefrigeration cycle circuit is configured. In the refrigeration cyclecircuit, the working fluid (refrigerant) is sealed.

Next, a configuration of refrigeration cycle device 101 will bedescribed.

As condenser 103 and evaporator 105, in a case where a surroundingmedium is air, a fin and tube type heat exchanger or a parallel flowtype (micro tube type) heat exchanger are used.

Meanwhile, as condenser 103 and evaporator 105 in a case where thesurrounding medium is brine or a refrigerant of two-dimensional typerefrigeration cycle device, a double pipe heat exchanger, a plate typeheat exchanger, or a shell and tube type heat exchanger, are used.

As expansion valve 104, for example, an electronic expansion valve whichuses a pulse motor driving method, or the like is used.

In refrigeration cycle device 101, in condenser 103, fluid machinery 107a which is a first transporting portion and drives (flows) thesurrounding medium (first medium) which exchanges heat with therefrigerant to a heat exchanging surface of condenser 103, is installed.In addition, in evaporator 105, fluid machinery 107 b which is a secondtransporting portion and drives (flows) the surrounding medium (secondmedium) which exchanges heat with the refrigerant to a heat exchangingsurface of evaporator 105, is installed. In addition, flow path 116 ofthe surrounding medium is provided in each of the surrounding mediums.

Here, as the surrounding medium, when the air in the atmosphere is used,there is a case where water or brine, such as ethylene glycol, is used.In addition, in a case where refrigeration cycle device 101 is thetwo-dimensional type refrigeration cycle device, a refrigerant which ispreferable for the refrigeration cycle circuit and a working temperatureregion, for example, hydrofluorocarbons (HFC), hydrocarbons (HC), orcarbon dioxide, is used.

As fluid machineries 107 a and 107 b which drive the surrounding medium,in a case where the surrounding medium is air, an axial flow blower,such as a propeller fan, a cross flow fan, or a centrifugal blower, suchas a turbo blower, is used, and in a case where the surrounding mediumis brine, a centrifugal pump is used. In addition, in a case whererefrigeration cycle device 101 is a two-dimensional type refrigerationcycle device, as fluid machineries 107 a and 107 b for transporting thesurrounding medium, compressor 102 plays a role thereof.

In condenser 103, at a location (hereinafter, in the specification,referred to as “two-phase pipe of condenser”) at which the refrigerantthat flows in the inside thereof flows in two phases (a state where gasand liquid are mixed with each other), condensation temperaturedetecting portion 110 a is installed, and it is possible to measure thetemperature of the refrigerant.

In addition, between an outlet of condenser 103 and an inlet ofexpansion valve 104, condenser outlet temperature detecting portion 110b is installed. Condenser outlet temperature detecting portion 110 b candetect overcooling degree (a value obtained by subtracting thetemperature of condenser 103 from an inlet temperature of expansionvalve 104) of inlet of expansion valve 104.

In evaporator 105, at a location (hereinafter, in the specification,referred to as “two-phase pipe of evaporator”) at which the refrigerantthat flows in the inside thereof flows in two phases, evaporationtemperature detecting portion 110 c is provided, and it is possible tomeasure the temperature of the refrigerant in the inside of evaporator105.

In a suction portion (between an outlet of evaporator 105 and an inletof compressor 102) of compressor 102, suction temperature detectingportion 110 d is provided. Accordingly, it is possible to measure thetemperature (suction temperature) of the refrigerant suctioned tocompressor 102.

In a case where, for example, an electronic thermostat which isconnected to the working fluid in a contact state at the piping in whichthe refrigerant flows or an outer pipe of a heat transfer pipe is usedas each of the above-described temperature detecting portion, there isalso a case where a sheath pipe type electronic thermostat whichdirectly comes into contact with the working fluid, is used.

Between the outlet of condenser 103 and the inlet of expansion valve104, high-pressure side pressure detecting portion 115 a which detects apressure on a high pressure side (a region in which the refrigerant fromthe outlet of compressor 102 to the inlet of expansion valve 104 ispresent at a high pressure) of the refrigeration cycle circuit, isinstalled.

At the outlet of expansion valve 104, low-pressure side pressuredetecting portion 115 b which detects a pressure on a low pressure side(a region in which the refrigerant from the outlet of expansion valve104 to the inlet of compressor 102 is present at a low pressure) of therefrigeration cycle circuit, is installed.

As high-pressure side pressure detecting portion 115 a and low-pressureside pressure detecting portion 115 b, for example, a member whichconverts displacement of a diaphragm into an electric signal, or thelike is used. In addition, instead of high-pressure side pressuredetecting portion 115 a and low-pressure side pressure detecting portion115 b, a differential pressure gauge (measuring means for measuring apressure difference between the outlet and the inlet of expansion valve104), may be used.

In addition, in the above-described description of the configuration, anexample in which refrigeration cycle device 101 is provided with all ofeach temperature detecting portion and each pressure detecting portion,is described, but in control which will be described later, a detectingportion which does not use a detected value can be omitted.

Next, a control method of refrigeration cycle device 101 will bedescribed. First, control when a general operation is performed will bedescribed.

When a general operation is performed, the overheating degree of theworking fluid at the suction portion of compressor 102, which is atemperature difference between suction temperature detecting portion 110d and evaporation temperature detecting portion 110 c, is computed. Inaddition, expansion valve 104 is controlled so that the overheatingdegree becomes a target overheating degree (for example, 5K) determinedin advance.

In addition, at a discharge portion of compressor 102, a dischargetemperature detecting portion (not illustrated) is further provided, andit is possible to perform the control by using the detected vale. Inthis case, the overheating degree of the working fluid at the dischargeportion of compressor 102, which is a temperature difference between thedischarge temperature detecting portion and condensation temperaturedetecting portion 110 a, is computed. In addition, expansion valve 104is controlled so that the overheating degree becomes a targetoverheating degree determined in advance.

Next, control in a case where a possibility of occurrence of adisproportionation reaction increases, and a special operation state isachieved, will be described.

In the embodiment, in a case where a temperature detected value ofcondensation temperature detecting portion 110 a becomes excessive,control of opening expansion valve 104, and decreasing the pressure andthe temperature of the high-pressure side working fluid in the inside ofrefrigeration cycle device 101, is performed.

In general, it is necessary to perform the control so that asupercritical condition which exceeds a critical point (a pointdescribed as T_(cri) in FIG. 15 which will be described later) is notachieved by the refrigerant excluding carbon dioxide. This is because,in a supercritical state, a material is placed in a state where eithergas or liquid is not present, and the behavior thereof is unstable andactive.

Here, in the embodiment, considering a temperature (criticaltemperature) at the critical point as one criterion, using thetemperature, an opening degree of expansion valve 104 is controlled sothat the condensation temperature does not approach approximately avalue (5K) determined in advance. In addition, in a case where theworking fluid (mixed refrigerant) containing R1123 is used, by using thecritical temperature of the mixed refrigerant, the control is performedso that the temperature of the working fluid does not become equal to orgreater than the critical temperature (−5° C.).

FIG. 15 is a Mollier diagram illustrating an operation of refrigerationcycle device 101 in the second embodiment of the present invention. InFIG. 15, isotherm 108 and saturation liquid line and saturation vaporline 109 are illustrated.

In FIG. 15, a refrigeration cycle which is under an excessive pressurecondition which becomes a cause of occurrence of a disproportionationreaction, is illustrated by a solid line (EP), and a refrigeration cyclewhich is under a normal operation condition, is illustrated by a brokenline (NP).

If a temperature value in condensation temperature detecting portion 110a provided in two-phase pipe of condenser 103 is equal to or less than5K (EP in FIG. 15) with respect to the critical temperature stored in acontrol device in advance, the control device controls the openingdegree of expansion valve 104 to be high. As a result, similar to NP ofFIG. 15, since the condensation pressure which is on the high-pressureside of refrigeration cycle device 101 decreases, it is possible tosuppress a disproportionation reaction which occurs due to an excessivepressure rise of the refrigerant, or to suppress the pressure rise evenin a case where a disproportionation reaction occurs.

In addition, the above-described control method is a method forcontrolling the opening degree of expansion valve 104 by indirectlygrasping the pressure in the inside of condenser 103 from thecondensation temperature measured by condensation temperature detectingportion 110 a. The method is particularly preferable since it ispossible use the condensation temperature as a target instead of thecondensation pressure in a case where the working fluid containing R1123is azeotrope or pseudoazeotrope, and a temperature difference(temperature gradient) between a dew point and a boiling point of theworking fluid containing R1123 in condenser 103, is zero or small.

Modification Example 1 of Control Method

In addition, as described above, by comparing the critical temperatureand the condensation temperature, by indirectly detecting a highpressure state (the pressure of the refrigerant in the inside ofcondenser 103) of refrigeration cycle device 101, instead of the controlmethod which commands an appropriate operation to expansion valve 104 orthe like, based on the pressure which is directly measured, a method forcontrolling the opening degree of expansion valve 104 may be used.

FIG. 16 is a Mollier diagram illustrating a control operation ofModification Example 1 in the second embodiment of the presentinvention.

In FIG. 16, from the discharge portion of compressor 102 to the inletsof condenser 103 and expansion valve 104, the refrigeration cycle in astate where an excessive pressure rise continues to be generated, isillustrated by a solid line (EP), and the refrigeration cycle in a statewhich is out of the above-described excessive-pressure state, isillustrated by a broken line (NP).

In the operation, in a case where a pressure difference obtained bysubtracting, for example, a pressure P_(cond) at the outlet of condenser103 detected by high-pressure side pressure detecting portion 115 a froma pressure (critical pressure) P_(cri) at the critical point stored inthe control device in advance, is smaller than a value (for example,Δp=0.4 MPa) determined in advance (EP of FIG. 16), from the dischargeport of compressor 102 to the inlet of expansion valve 104, bydetermining that a disproportionation reaction occurs in the workingfluid containing R1123, or there is a concern about occurrence of adisproportionation reaction, the opening degree of expansion valve 104is controlled to be high to avoid continuity under the high-pressurecondition.

As a result, as illustrated by NP in FIG. 16, the refrigeration cycle inFIG. 16 acts on the high pressure (condensation pressure) to decrease,and it is possible to suppress the pressure rise that causes occurrenceof a disproportionation reaction and occurs after a disproportionationreaction.

In the working fluid containing R1123, it is preferable to use thecontrol method in a case of a non-azeotropic state, in particular, in acase where a temperature gradient is large in the condensation pressure.

Modification Example 2 of Control Method

In addition, instead of the control method using the above-describedcritical temperature or the critical pressure as a standard, a controlmethod based on the overcooling degree may be used.

FIG. 17 is a Mollier diagram illustrating a control operation ofModification Example 2 of the control method of refrigeration cycledevice 101 in the second embodiment of the present invention.

In FIG. 17, the refrigeration cycle which is under an excessive pressurecondition which is a cause of occurrence of a disproportionationreaction, is considered as EP, and is illustrated by a solid line, andthe refrigeration cycle which is under a normal operation is consideredas NP, and is illustrated by a broken line.

In general, in refrigeration cycle device 101, by appropriatelycontrolling the refrigeration cycle of expansion valve 104 or compressor102, and by making the size of the heat exchanger and the refrigerantfilling amount appropriate, the temperature of the refrigerant in theinside of condenser 103 is set so that the temperature increases by acertain degree with respect to the surrounding medium. In addition, ingeneral, the overcooling degree is a value which is approximately 5K.Even in the working fluid which is similarly used in refrigeration cycledevice 101 and contains R1123, similar measures are taken.

In refrigeration cycle device 101 in which the above-described measureis taken, if the pressure of refrigerant is excessively high, there isalso a tendency for the overcooling degree of the inlet of expansionvalve 104 to increase as illustrated by EP of FIG. 17. In addition, inthe embodiment, considering the overcooling degree of the refrigerant ofthe inlet of expansion valve 104 as a standard, the opening degree ofexpansion valve 104 is controlled.

In addition, in the embodiment, considering the overcooling degree ofthe refrigerant at the inlet of expansion valve 104 when the normaloperation is performed as 5K, using 15K which is three times the valueas a criterion, the opening degree of expansion valve 104 is controlled.The overcooling degree which is a threshold value is three times thevalue, because there is a possibility that the overcooling degreechanges within the range according to the operation condition.

Specifically, first, the overcooling degree is calculated from thedetected value of condensation temperature detecting portion 110 a andthe detected value of condenser outlet temperature detecting portion 110b. The overcooling degree is a value obtained by subtracting thedetected value of condenser outlet temperature detecting portion 110 bfrom the detected value of condensation temperature detecting portion110 a. In addition, when the overcooling degree at the inlet ofexpansion valve 104 reaches the value (15K) determined in advance, anoperation of controlling the opening degree of expansion valve 104 to behigh is performed, and the condensation pressure at a high-pressure partof refrigeration cycle device 101 is controlled to decrease (from asolid line to a broken line of FIG. 17).

Since the decrease in condensation pressure is the same as the decreasein condensation temperature, the condensation temperature decreases fromT_(cond1) to T_(cond2), and the overcooling degree at the inlet ofexpansion valve 104 decreases from T_(cond1)−T_(exin) toT_(cond2)−T_(exin) (here, a working fluid temperature of the inlet ofexpansion valve 104 does not change, and is T_(exin)). As describedabove, since the overcooling degree also decreases according to thedecrease in condensation pressure in the inside of refrigeration cycledevice 101, it is understood that the control in condensation pressurein the inside of refrigeration cycle device 101 is possible even in acase where the overcooling degree is considered as a standard.

FIG. 18 is a view illustrating piping joint 117 which configures a partof the piping of refrigeration cycle device 101 of the second embodimentof the present invention.

In a case where refrigeration cycle device 101 of the present inventionis used, for example, in home spilt type air conditioner (airconditioner), the refrigeration cycle device 101 is configured of anoutdoor unit including an outdoor heat exchanger and an indoor unitincluding an indoor heat exchange. The outdoor unit and the indoor unitcannot be integrated with each other in the configuration. Accordingly,by using a mechanical joint which is illustrated in FIG. 18 similar tounion flare 111, the outdoor unit and the indoor unit are connected toeach other at an installation location.

If a connection state of the mechanical joint deteriorates due to acause when the work is not sufficient, or the like, the refrigerantleaks from the joint part, and this causes the negative influence on theequipment performance. In addition, since the working fluid containingR1123 itself is greenhouse gas having a greenhouse effect, there is alsoa concern about a negative influence on global environment. Accordingly,the refrigerant leakage is rapidly detected and repaired.

Examples of a method for detecting the refrigerant leakage include amethod of coating the part with a detection agent, and detecting whetheror not bubbles are generated, and a method of using a detection sensor,but it takes time and effort in each method.

Here, in the embodiment, by winding seal 112 containing a polymerizationpromoter on an outer circumference of union flare 111, the detection ofrefrigerant leakage becomes easy, and reduction of leakage amount isachieved.

Specifically, in the working fluid containing R1123, when polymerizationreaction occurs, generation of polytetrafluoroethylene which is one of afluorinated carbon resin is used. Specifically, by intentionallybringing the working fluid containing R1123 and polymerization promoterinto contact with each other at the location of leakage, at the locationof leakage, polytetrafluoroethylene is configured to be extracted andsolidified. As a result, since the leakage is likely to be detectedeasily and visually, it is possible to shorten the time which is takenfor finding the leakage and performing the repair.

Furthermore, since a part at which polytetrafluoroethylene is generatedis a part of leakage of the working fluid containing R1123,spontaneously, since a polymerization product is generated and adheresto a part at which the leakage is prevented, it is also possible toreduce the leakage amount.

Third Embodiment

Next, a third embodiment of the present invention will be described.

FIG. 19 is a view illustrating a configuration of refrigeration cycledevice 130 according to a third embodiment of the present invention.

Refrigeration cycle device 130 illustrated in FIG. 19 and refrigerationcycle device 101 of the second embodiment, are different from each otherin that bypass pipe 113 provided with an opening and closing valve, andis connected to the inlet and the outlet of expansion valve 104 is newlyinstalled. In addition, refrigeration cycle device 130 and refrigerationcycle device 101 are also different from each other in that a purge linehaving relief valve 114 is provided between the outlet of condenser 103and the inlet of expansion valve 104. The opening side of relief valve114 is disposed outdoor. In addition, in FIG. 19, description of eachtemperature detecting portion and each pressure detecting portion whichare described by using FIG. 14, is omitted.

By performing a control method (for example, a control method forcontrolling the opening degree of expansion valve 104 so that a valueobtained by subtracting the working fluid temperature measured by thetwo-phase tube of condenser 103 from the critical temperature of theworking fluid containing R1123 is equal to or greater than 5K, or acontrol method for performing the control so that a difference betweenthe critical pressure of the working fluid and the pressure detected byhigh-pressure side pressure detecting portion 115 a is equal to orgreater than 0.4 MPa) described in the second embodiment, even in a casewhere the opening degree of expansion valve 104 is high, there is apossibility that a case where the decrease in pressure is not improved,or a situation in which a speed of decrease in pressure is desired to beraised, occur.

Here, in a case where the above-described situation is generated, byopening the opening and closing valve provided in bypass pipe 113 of theembodiment, and by allowing the refrigerant to flow to bypass pipe 113,the pressure of the working fluid on a high pressure side rapidlydecreases and it is possible to suppress damage of refrigeration cycledevice 130.

Furthermore, in addition to the control of increasing the opening degreeof expansion valve 104, and the control of the opening and closing valveprovided in bypass pipe 113, the control is more preferable since damageof refrigeration cycle device 130 is prevented if compressor 102 isemergency-stopped. In addition, in a case where compressor 102 isemergency-stopped, it is preferable not to stop fluid machineries 107 aand 107 b since the pressure of the working fluid on the high-pressureside rapidly decreases.

Even in a case where the above-described response is performed, a casewhere a disproportionation reaction is not suppressed, specifically, acase where a difference between the critical temperature of the workingfluid and the condensation temperature detected by condensationtemperature detecting portion 110 a is less than 5K, or a case where adifference between the critical pressure of the working fluid and thepressure detected by high-pressure side pressure detecting portion 115 ais less than 0.4 MPa, are assumed. In this case, since there is aconcern that the pressure of the refrigerant in the inside ofrefrigeration cycle device 130 increases, a necessity of releasing therefrigerant of which the pressure is high to the outside, and preventingdamage of refrigeration cycle device 130, is generated. Here, reliefvalve 114 which purges the working fluid containing R1123 in the insideof refrigeration cycle device 130 to an outer space, is controlled toopen.

Here, it is preferable that an installation position of relief valve 114in refrigeration cycle device 130 is on a high-pressure side.Furthermore, it is particularly preferable that relief valve 114 isinstalled from the outlet of condenser 103 illustrated in the embodimentto the inlet of expansion valve 104 (at this position, since the workingfluid is in a high-pressure overcooling liquid state, a water hammeringaction which causes a result of rapid pressure rise according to adisproportionation reaction is likely to occur), or relief valve 114 isinstalled from the discharge portion of compressor 102 to the inlet ofcondenser 103 (at this position, since the working fluid is present in ahigh-temperature and high-pressure gas state, a molecular motion becomesactive, and a disproportionation reaction is likely to occur).

Relief valve 114 is provided on the outdoor unit side. In this case, theaspect is called an aspect which is considered not to directly influencea human and commodity, since a configuration in which the working fluidis not emitted to a residential space on the indoor side in a case ofthe air conditioner, and the working fluid is not emitted to a productdisplay side, such as a showcase, in a case of a freezing andrefrigeration unit, is possible.

In addition, it is preferable to turn off a power source, for example,to open relief valve 114 and stop refrigeration cycle device 130, fromthe viewpoint of safety.

Fourth Embodiment

Next, a fourth embodiment of the present invention will be described.

FIG. 20 is a view illustrating a configuration of refrigeration cycledevice 140 according to the fourth embodiment of the present invention.

Refrigeration cycle device 140 illustrated in FIG. 20 and refrigerationcycle device 101 of the second embodiment are different from each otherin that first medium temperature detecting portion 110 e which detectsthe temperature of the first medium before flowing into condenser 103,and second medium temperature detecting portion 110 f which detects thetemperature of the second medium before flowing into evaporator 105, areprovided. Furthermore, the detected values of each temperature detectingportion and each pressure detecting portion, and input power ofcompressor 102 and fluid machineries 107 a and 107 b, are stored in anelectronic storage device (not illustrated) for a certain period oftime.

FIG. 21 is a view illustrating an operation of refrigeration cycledevice 140 of the fourth embodiment of the present invention in aMollier diagram.

In FIG. 21, the refrigeration cycle illustrated by EP is thecondensation pressure when a disproportionation reaction occurs, and therefrigeration cycle illustrated by NP indicates the refrigeration cyclewhen the normal operation is performed. In addition, in FIG. 21, inorder to make the description simple, a cycle change (example: adifference in evaporation pressures between NP and EP) when thecondensation pressure increases is not described.

As a reason of a rapid increase in the condensation temperature of theworking fluid containing R1123 which is measured in the two-phase pipein the inside of condenser 103, (1) a rapid increase in surroundingmedium temperatures T_(mcon) and T_(meva), (2) a pressure rise actiondue to an increase in power of compressor 102, and (3) a change in flow(a change in power of any of fluid machineries 107 a and 107 b whichdrives the surrounding medium) of the surrounding medium, areconsidered. In addition, as a specific phenomenon of the working fluidcontaining R1123, (4) a pressure rise action due to a disproportionationreaction is employed. Here, in the embodiment, in order to specify thata disproportionation reaction occurs of (4), the control is performedafter determining that phenomenon of (1) to (3) does not occur.

Here, in the control method of the embodiment, in a case where an amountof change in the condensation temperature of the working fluidcontaining R1123 with respect to an amount of change in temperature orinput power of (1) to (3), expansion valve 104 is controlled to open.

Hereinafter, a specific control method will be described. First, sinceit is difficult to compare the amount of change in temperature and theamount of change in input power value with each other under the samestandard, when measuring the amount of change in temperature, the inputpower is controlled not to change. In other words, when measuring theamount of change in temperature, a motor rotation speed of compressor102 and fluid machineries 107 a and 107 b are maintained to be constant.

For example, the amount of change in temperature is measured at acertain time interval, for example, for 10 seconds to 1 minute. Beforethe measurement, for example, approximately 10 seconds to 1 minute ago,the amount of input power of compressor 102 and fluid machineries 107 aand 107 b is controlled to be maintained to a certain value. At thistime, an amount of change per unit time of the amount of input power ofcompressor 102 and fluid machineries 107 a and 107 b substantiallybecomes zero. Here, the amount is “substantially” zero because a changein a suctioned state of compressor 102 due to deviation of refrigerantin compressor 102, or a slight change in input power due to influence ofblowing of wind or the like in a case where the first medium and thesecond medium are surrounding air in fluid machineries 107 a and 107 b,are generated. In other words, the “substantially zero” means that theamount of change includes a slight behavior and is smaller than apredetermined value determined in advance.

Under the above-described condition, in a case where the amount ofchange per unit time of the condensation temperature measured bycondensation temperature detecting portion 110 a is greater than any ofthe amount of change per unit time of the temperature of the firstmedium detected by first medium temperature detecting portion 110 e, andthe amount of change per unit time of the temperature of the secondmedium detected by second medium temperature detecting portion 110 f, itis considered that a disproportionation reaction occurs, expansion valve104 is controlled to open.

In addition, only in controlling the opening degree of expansion valve104, to be prepared for a case where the pressure rise generatedaccording to a disproportionation reaction cannot be controlled, similarto the third embodiment, bypass pipe 113 may be provided in parallelwith expansion valve 104, compressor 102 may be emergency-stopped, andfurther, means, such as relief valve 114, which reduces the pressure byemitting the refrigerant to the outside may be provided.

In addition, in the embodiment, a control example of expansion valve 104in which control is performed considering the amount of change of thetemperature detecting portion installed in the two-phase pipe ofcondenser 103 as a standard, but an amount of change in pressure at anypoint from the discharge portion of compressor 102 to the inlet ofexpansion valve 104 may be considered as a standard, and an amount ofchange in overcooling degree of the inlet of expansion valve 104 may beconsidered as a standard.

In addition, using the embodiment being combined with any of theabove-described second embodiment or the third embodiment, is preferablesince it is possible to further improve the reliability.

Fifth Embodiment

Next, a fifth embodiment of the present invention will be described.

FIG. 22 is a view in which main portions of compression mechanismportion 2 of scroll compressor 200 according to the fifth embodiment ofthe present invention are enlarged.

Since the embodiment is the same as the first embodiment except thepresence and absence of reed valve 19 provided in discharge hole 18,description of configurations other than this will be omitted.

In the first embodiment, similar to bypass hole 68, reed valve 19 (checkvalve) is provided in discharge hole 18, but in the embodiment, reedvalve 19 is not provided in discharge hole 18. Therefore, dischargechamber 31 always communicates with compression chamber 15 in thevicinity thereof via discharge hole 18, and discharge chamber 31 andcompression chamber 15 are placed in a substantially same pressurestate. In addition, in the embodiment, since reed valve 19 is notprovided in discharge hole 18, valve stop 69 is also not provided,either.

Since a condition in which a disproportionation reaction is particularlylikely to occur is a condition under an excessive high temperature andhigh pressure, there is a case where a state where the condition is nota predetermined operation condition, for example, a state where therefrigerant piping in the refrigeration cycle circuit is blocked,blowing of the condenser is stopped, and the discharge pressure(high-pressure side of the refrigeration cycle circuit) excessivelyincreases due to forgetting of opening of two-way valve or three-wayvalve, or a state where the compression mechanism does not performcompression work of increasing the pressure of the refrigerant due toinsufficient torque of an electric motor (motor portion 3) of thecompressor, is generated.

Under the condition, when the power continues to be supplied to scrollcompressor 200, a current is excessively supplied to the electric motorwhich configures scroll compressor 200, and the electric motor generatesheat. As a result, the electric motor in scroll compressor 200 is usedas a heating element with respect to the refrigerant, and the pressureand the temperature of the refrigerant in the inside excessivelyincreases. As a result, an insulator of the winding wire whichconfigures a stator of the electric motor is dissolved, core wires(conducting wire) of the winding wire come into contact with each other,and a phenomenon which is called layer short-circuit occurs. Since highenergy is instantaneously transferred to the surrounding refrigerant,the layer short-circuit can become a starting point of adisproportionation reaction.

Here, in the embodiment, even in a case where the power continues to besupplied to the electric motor while the compression mechanism does notperform a pressure rise operation, an aspect in which the pressure riseof airtight container 1 which accommodates the electric motor, that is,on the high-pressure side of the refrigeration cycle, is suppressed, anda condition of occurrence of a disproportionation reaction is avoided bythe pressure, is achieved. Specifically, discharge chamber 31 isconfigured to always communicate with compression chamber 15 in thevicinity via discharge hole 18.

As described above, according to the embodiment, in a case where thepower continues to be supplied to the electric motor while thecompression mechanism does not perform the compression operation, theelectric motor heats the refrigerant in the inside of airtight container1 as a heating element. However, for example, even when the pressure ofthe refrigerant increases due to the heating, the pressure acts oncompression chamber 15 via discharge hole 18, it is possible to releasethe pressure in the inside of airtight container 1 to the low-pressureside of the refrigeration cycle circuit by reversely rotating thecompression mechanism, and therefore, it is possible to avoid anabnormal pressure rise which becomes a condition of occurrence of adisproportionation reaction.

As described above, in a first aspect illustrated from the firstembodiment to the fifth embodiment of the present invention, acompression chamber which is formed in both directions by meshing thefixed scroll and the revolving scroll in which a spiral lap from the endplate rises with each other by using a refrigerant containing1,1,2-trifluoroethylene as a working fluid, and by using the polyvinylether oil as a compressor lubricating oil, is provided. In addition, atthe center position of the end plate of the fixed scroll, the dischargehole which is open to the discharge chamber, and the bypass hole whichcommunicates with the compression chamber and the discharge chamberbefore the compression chamber communicates with the discharge hole, onthe end plate of the fixed scroll. Furthermore, in the bypass hole, thecheck valve which allows the flow from the compression chamber side tothe discharge chamber side is provided.

According to this configuration, since it is possible to suppress thetemperature rise due to excessive compression in the refrigerantimmediately before being ejected from the discharge hole, it is possibleto suppress a disproportionation reaction of R1123. In addition, sincethe polyvinyl ether oil has a relatively low polarity, and it is easy toachieve an effect of improving slidability by the additive, it ispossible to suppress local heat generation in the sliding portion, andto suppress self-degradable reaction of R1123.

In addition, a plurality of bypass holes may be provided. Accordingly, asection in which the bypass hole and the compression chamber communicatewith each other becomes a wider range, and only by the total area offlow path of the bypass hole which is effective at the same time, it ispossible to reduce each resistance of the flow path, and it is possibleto obtain an effect of reliably suppressing the temperature rise causedby the excessive compression.

In addition, among the bypass holes, at least one bypass hole may be acircular communication hole. Accordingly, it is possible to minimize theresistance of the flow path with respect to the area of the bypass hole,and to obtain an effect of further suppressing the temperature risecaused by the excessive compression.

In addition, among the bypass holes, at least one bypass hole may beprovided at a position at which the bypass hole is open in any of thefirst compression chamber which is formed on the lap outer wall side ofthe revolving scroll, or the second compression chamber which is formedon the lap inner wall side of the revolving scroll.

Accordingly, each of the compression chambers reaches the dischargepressure, and opens the check valve of a bypass hole, the bypass holecan be provided at an appropriate position, and it is possible to obtainan effect of minimizing the temperature rise caused by the excessivecompression.

In addition, among the bypass holes, at least one bypass hole may beprovided at a position at which the bypass hole is open in both of thefirst compression chamber which is formed on the lap outer wall side ofthe revolving scroll and the second compression chamber which is formedon the lap inner wall side of the revolving scroll, and the bypass holemay have a size and a shape which is not open in the first compressionchamber and second compression chamber at the same time.

Accordingly, the first compression chamber and the second compressionchamber communicate with each other via the bypass hole, the workingrefrigerant re-expands from the pressure difference, and it is possibleto prevent the temperature in the inside of the compression chamber fromincreasing.

In addition, among the bypass holes, when a diameter of bypass hole is Dand a length in the thickness direction of the end plate is L, at leastone bypass hole may be configured to be D/L is in a range of 2.4 to 7.2.

Accordingly, it is possible to provide a compressor which optimize aratio between loss in pressure of the working refrigerant thatcommunicates with the bypass hole, and loss caused by re-expansion ofthe working fluid in the inside of the bypass hole, and which highlyefficiently suppresses the temperature rise in the inside of thecompression chamber.

Next, a second aspect may be a configuration in which the check valve isthe reed valve provided on the end plate surface of the fixed scroll inthe check valve in the first aspect.

Accordingly, compared to the check valve provided with a spring or thelike in the inside of the bypass hole, it is possible to obtain aneffect of suppressing the resistance of the flow path and therebysuppressing the temperature rise caused by the excessive compression.

In addition, in a third aspect, in the first aspect or the secondinvention, the working fluid may be a mixed working fluid containingdifluoromethane, and difluoromethane may be 30% by weight to 60% byweight. In addition, the working fluid may be a mixed working fluidcontaining tetrafluoroethane, and tetrafluoroethane may be 30% by weightto 60% by weight. In addition, the working fluid may be a mixed workingfluid containing difluoromethane and tetrafluoroethane, anddifluoromethane may be mixed with tetrafluoroethane, and proportions ofdifluoromethane and tetrafluoroethane may be 30% by weight to 60% byweight.

According to this, it is possible to suppress a disproportionationreaction of R1123, and to improve a refrigeration performance or COP.

In a fourth aspect, in any one aspect among the first to third aspects,the polyvinyl ether oil may contain a phosphate ester anti-wear agent.

According to this, as the anti-wear agent is adsorbed to the frontsurface of the sliding portion and reduces wear, it is possible tosuppress heat generation, and to suppress self-degradable reaction ofthe refrigerant R1123.

In a fifth aspect, in any one aspect among the first to third aspects,the polyvinyl ether oil may contain the phenolic antioxidant.

According to this, since the phenolic antioxidant rapidly captures theradicals generated by the sliding portion, it is possible to prevent theradicals from reacting to the refrigerant R1123.

In a sixth aspect, in any one of the first to third aspects, thepolyvinyl ether oil may be lubricating oil which is obtained by mixing alubricating oil having a higher viscosity than that of the base oil witha terpene type or a terpenoid type of which an amount is equal to orgreater than 1% and less than 50%, or is obtained by mixing alubricating oil having a super-high viscosity of which an amount isequal to or greater than that of a terpene type or a terpenoid type inadvance therewith, and by mixing an oil additive of which the viscosityis adjusted to be equivalent to that of the base oil with the base oil.

According to this, it is possible to suppress a disproportionationreaction of R1123.

In a seventh aspect, in any one of the first to third aspects, a motorportion may use an electrical wire which is obtained by coating aconductor with the thermosetting insulating material and baking with theinsulating film therebetween, as a coil.

According to this, by coating the winding wire of the coil for theelectric motor in the compressor with the thermosetting insulatingmaterial, while maintaining high resistance between the winding wireseven in a state where the coil infiltrates into the liquid refrigerant,it is possible to suppress the discharge, and as a result, to suppressdecomposition of the refrigerant R1123.

In an eighth aspect, in any one of the first to third aspects, anairtight container may include a power supply terminal which isinstalled in a mouth portion via the insulating member, and theconnection terminal for connecting the power supply terminal to a leadwire. In addition, the doughnut-like insulating member which adheres tothe insulating member may be pipe-connected to the power supply terminalon an inner side of the airtight container.

According to this, since the insulating member is added to the powersupply terminal on the inner side of the metal housing, by extending theshortest distance between conductors, it is possible to suppress aninsulation defect of the power supply terminal, and to prevent ignitiondue to the discharge energy of R1123. In addition, it is possible toprevent a hydrogen fluoride generated when R1123 is decomposed fromcoming into contact with a glass insulating material, and to prevent theglass insulating material from corroding and being damaged.

In a ninth aspect, in the first to eighth aspects, the refrigerationcycle device is a refrigeration cycle device, in which the compressor ofany one of aspects; the condenser which cools a refrigerant gas that iscompressed by the compressor and has a high pressure; the throttlemechanism which reduces the pressure of the high-pressure refrigerantwhich is liquefied by the condenser; and the evaporator which gasifiesthe refrigerant of which the pressure is reduced by the throttlemechanism, are linked to each other by the piping.

According to this, it is possible to suppress a disproportionationreaction of R1123, to improve a refrigeration performance and COP.

In a tenth aspect, in the ninth aspect, the condensation temperaturedetecting portion provided in the condenser may be provided, and adifference between the critical temperature of the working fluid and thecondensation temperature detected by the condensation temperaturedetecting portion may control the opening degree of the throttlemechanism to become equal to or greater than 5K.

According to this, by making the working fluid temperature measured bythe temperature detecting portion correspond to the pressure, it ispossible to control the opening degree of the throttle mechanism tolimit the working fluid temperature (pressure) on a high-pressure sideto be equal to or greater than 5K considering a margin of safety fromthe critical pressure.

Accordingly, since it is possible to prevent the higher condensationpressure from excessively increasing, as a result (result in which thedistance by which the molecules approach each other), it is possible tosuppress a disproportionation reaction which suppresses adisproportionation reaction which is a concern to be generated, and toensure the reliability of the device.

In an eleventh aspect, in the ninth aspect, the high-pressure sidepressure detecting portion provided between the discharge portion of thecompressor and the inlet of the throttle mechanism, may be provided, andthe difference between the critical pressure of the working fluid andthe pressure detected by the high-pressure side pressure detectingportion may control the degree of the throttle mechanism to be equal toor greater than 0.4 MPa.

According to this, regarding the working fluid containing R1123, inparticular, in a case where a non-zeotropic refrigerant having a largetemperature gradient is used, it is possible to more accurately detectthe pressure of the refrigerant, and further, to decrease the pressure(condensation pressure) on the high-pressure side in the refrigerationcycle device by performing the control of the opening degree of thethrottle mechanism by using the detection result. Accordingly, it ispossible to suppress a disproportionation reaction, and to improve thereliability of the device.

In a twelfth aspect, in the ninth aspect, the condenser outlettemperature detecting portion provided between the condenser and thethrottle mechanism may be provided, and may control the opening degreeof the throttle mechanism so that the difference between thecondensation temperature detected by the condensation temperaturedetecting portion and the condenser output temperature detected by thecondenser outlet temperature detecting portion is equal to or less than15K.

According to this, by using the detection result of the overcoolingdegree illustrated by the difference between the condensationtemperature detecting portion and the condenser outlet temperaturedetecting portion, it is possible to perform the control of the openingdegree of the throttle mechanism, and to prevent the pressure of theworking fluid in the inside of the refrigeration cycle device fromexcessively increasing. Accordingly, it is possible to suppress adisproportionation reaction, and to improve the reliability of thedevice.

In a thirteenth aspect, in the ninth aspect, the first transportingportion which transports the first medium that exchanges the heat in thecondenser, a second transporting portion which transports the secondmedium that exchanges the heat in the evaporator, the condensationtemperature detecting portion which is provided in the condenser, thefirst medium temperature detecting portion which detects the temperatureof the first medium before flowing into the condenser, and the secondmedium temperature detecting portion which detects the temperature ofthe second medium before flowing into the evaporator, are provided. Inaddition, a case where at least any one of the amount of change per unittime of the input of the compressor, the amount of change per unit timeof the input of the first transporting portion, and the amount of changeper unit time of the input of the second transporting portion, issmaller than a predetermined value determined in advance. In addition,in a case where the amount of change per unit time of the temperature ofthe first medium detected by the first medium temperature detectingportion is greater than any one of the amount of change per unit time ofthe condensation temperature detected by the condensation temperaturedetecting portion, and the amount of change per unit time of thetemperature of the second medium detected by the second mediumtemperature detecting portion, the throttle mechanism may be controlledin the opening direction.

According to this, in a case where an aspect of the surrounding mediumdoes not change, in a case where the condensation temperature rapidlychanges, since it is considered that the pressure increases due to adisproportionation reaction, the opening degree of the throttlemechanism can be controlled to be high. Accordingly, it is possible toimprove the reliability of the device.

In a fourteenth aspect, in any one of the ninth to thirteenth aspects,the outer circumference of the joint of the piping which configures therefrigeration cycle circuit may be covered with a sealing compoundcontaining the polymerization promoter.

According to this, in a case where the working fluid leaks from thejoint, the polymerization product is generated as polymerizationreaction is performed with respect to the polymerization promotercontained in the sealing compound and the working fluid containingR1123. Accordingly, the leakage is likely to be visually confirmed, thepolymerization product acts to prevent the flow of the refrigerantemitted to the outside, and it is possible to suppress the leakage ofthe refrigerant.

In a fifteenth aspect, in any one of the first to eighth aspects, thedischarge chamber may always communicate with the compression chambervia the discharge hole.

According to this, the power is supplied to the electric motor while thecompression mechanism does not perform the compression operation, theelectric motor heats the refrigerant in the inside of the airtightcontainer as the heat element, and even when the pressure of therefrigerant increases, the pressure acts on the compression chamber viathe discharge hole, and the pressure in the inside of the airtightcontainer is released to the low-pressure side of the refrigerationcycle circuit by reversely rotating the compression mechanism.Therefore, it is possible to avoid the abnormal pressure rise whichbecomes a condition of occurrence of a disproportionation reaction.

Sixth Embodiment

Next, a sixth embodiment of the present invention will be described.

FIG. 23 is a system configuration view of refrigeration cycle device1100 which uses compressor 161 according to the sixth embodiment of thepresent invention.

As illustrated in FIG. 23, refrigeration cycle device 1100 of theembodiment is mainly configured of compressor 161, condenser 162,throttle mechanism 163, and evaporator 164, for example, in a case of acycle exclusively for cooling. In addition, the equipment is linked toeach other so that a working fluid (refrigerant) circulates by piping.

In refrigeration cycle device 1100 configures as described above, therefrigerant changes to liquid by at least any of pressurizing andcooling, and changes to gas by at least any of pressurizing and heating.Compressor 161 is driven by the motor, and transports thelow-temperature and low-pressure gas refrigerant to condenser 162 bypressurizing the refrigerant to the high-temperature and high-pressuregas refrigerant. In condenser 162, the high-temperature andhigh-pressure gas refrigerant is cooled by air blown by a fan or thelike, is condensed, and becomes the low-temperature and high-pressureliquid refrigerant. The pressure of the liquid refrigerant is reduced bythrottle mechanism 163, a part of the liquid refrigerant becomes thelow-temperature and low-pressure gas refrigerant, a remaining partbecomes the low-temperature and low-pressure liquid refrigerant, and theliquid refrigerant is transported to evaporator 164. In evaporator 164,the low-temperature and low-pressure liquid refrigerant is heated andevaporated by the air blown by the fan or the like, becomes thelow-temperature and low-pressure gas refrigerant, is suctioned tocompressor 161 again, and is pressurized. The cycle is repeatedlyperformed.

In addition, in the description above, refrigeration cycle device 1100exclusively for cooling is described, but by using reversing valve orthe like, it is certainly possible to operate refrigeration cycle deviceas a cycle device for heating.

In addition, it is desirable that the heat transfer pipe whichconfigures the refrigerant flow path of the heat exchanger in at leastany of condenser 162 and evaporator 164, is the aluminum refrigerantpipe including aluminum or aluminum alloy. In particular, it isdesirable that the heat transfer pipe is the flattened pipe providedwith the plurality of refrigerant flows hole on a condition that thecondensation temperature decreases or the evaporation temperatureincreases.

The working fluid (refrigerant) which is sealed in refrigeration cycledevice 1100 of the embodiment is a two-component mixed working fluidmade of (1) R1123 (1,1,2-trifluoroethylene) and (2) R32(difluoromethane), and in particular, is a mixed working fluid in whichthere is 30% by weight to 60% by weight of R32.

In a case of employment to scroll compressor 1200 which will describedlater, by mixing 30% by weight or more of R32 with R1123, it is possibleto suppress a disproportionation reaction of R1123. As a concentrationof R32 increases, it is possible to further suppress adisproportionation reaction. This is because it is possible to suppressa disproportionation reaction of R1123 by an action of reducing a chanceof a disproportionation reaction due to integrated behaviors during aphase change, such as condensation and evaporation since an action ofR32 for mitigating a disproportionation reaction by small polarizationto a fluorine atom, and physical properties of R1123 and R32 are similarto each other.

In addition, the mixed refrigerant of R1123 and R32 can be handled as asingle refrigerant since the mixed refrigerant of R1123 and R32 has anazeotropic point when R32 is 30% by weight and R1123 is 70% by weight,and the temperature does not slip. In addition, when 60% by weight ormore of R32 is mixed with R1123, the temperature slide increases, andsince there is a possibility that it is difficult to handle the singlerefrigerant in a similar manner, it is desirable to mix 60% by weight orless of R32 with R1123. In particular, in order to preventdisproportionation, to further reduce the temperature slide whenapproaching the azeotropic point, and to easily design the equipment, itis desirable that R32 is mixed at a ratio of 40% by weight to 50% byweight with R1123.

FIGS. 24 and 25 are views comparing R410A and R1123 with each other bycomputing a refrigeration performance in a case where a pressure and atemperature in the refrigeration cycle, and a displacement volume of thecompressor are the same, and cycle efficiency (COP), at proportions of30% by weight to 60% by weight of R32, in a mixed working fluid of R1123and R32 in the sixth embodiment of the present invention.

First, the computation condition of FIGS. 24 and 25 will be described.In recent years, in order to improve the cycle efficiency of theequipment, the performance of the heat exchanger is improved, and in anactual operation state, there is a tendency for the condensationtemperature to decrease, and for the evaporation temperature toincrease, and there is also a tendency for the discharge temperature todecrease. Therefore, considering the actual operation condition, thecooling computation condition of FIG. 24 is a condition whichcorresponds to the time when the cooling operation of the airconditioner (the indoor dry-bulb temperature is 27° C., the wet-bulbtemperature is 19° C., and the outdoor dry-bulb temperature is 35° C.)is performed, and the evaporation temperature is 15° C., thecondensation temperature is 45° C., the overheating degree of suctionedrefrigerant of the compressor is 5° C., and the overcooling degree of anoutlet of the condenser is 8° C.

In addition, the heating computation condition of FIG. 25 is acomputation condition which corresponds to the time when the heatingoperation of the air conditioner (the indoor dry-bulb temperature is 20°C., the outdoor dry-bulb temperature is 7° C., and the dry-bulbtemperature is 6° C.) is performed, the evaporation temperature is 2°C., the condensation temperature is 38° C., the overheating degree ofsuctioned refrigerant of the compressor is 2° C., and the overcoolingdegree of an outlet of the condenser is 12° C.

As illustrated in FIGS. 24 and 25, by mixing R32 at a ratio of 30% byweight to 60% by weight with R1123, when performing the coolingoperation and the heating operation, comparing with R410A, it isascertained that a refrigeration performance increases approximately by20%, the cycle efficiency (COP) is 94 to 97%, and the global warmingpotential can be reduced to 10 to 20% of R410A.

As described above, in a two-component system of R1123 and R32, whencomprehensively considering prevention of disproportionation, the sizeof temperature slide, a performance when the cooling operation isperformed and when the heating operation is performed, and COP (that is,when specifying the proportions employed in the air conditioner whichuses scroll compressor 1200 that will be described later), the mixturecontaining R32 at a ratio of 30% by weight to 60% by weight isdesirable. More desirably, the mixture containing R32 at a ratio of 40%by weight to 50% by weight is desirable.

Modification Example 1 of Working Fluid

In addition, the working fluid sealed in refrigeration cycle device 1100of the embodiment is a two-component mixed working fluid made of (1)R1123 (1,1,2-trifluoroethylene) and (2) R125 (tetrafluoroethane), and inparticular, is a mixed working fluid in which there is 30% by weight to60% by weight of R125.

In a case of employment to scroll compressor 1200 which will describedlater, by mixing 30% by weight or more of R125 with R1123, it ispossible to suppress a disproportionation reaction of R1123. As aconcentration of R125 increases, it is possible to further suppress adisproportionation reaction. This is because it is possible to suppressa disproportionation reaction of R1123 by an action of reducing a chanceof a disproportionation reaction due to integrated behaviors during aphase change, such as condensation and evaporation since an action ofR125 for mitigating a disproportionation reaction by small polarizationto a fluorine atom, and physical properties of R1123 and R125 aresimilar to each other. In addition, since R125 is a nonflammablerefrigerant, R125 can reduce flammability of R1123.

FIGS. 26 and 27 are views comparing R410A and R1123 with each other bycomputing a refrigeration performance in a case where a pressure and atemperature in the refrigeration cycle, and a displacement volume of thecompressor are the same, and cycle efficiency (COP), at proportions of30% by weight to 60% by weight of R125, in a mixed working fluid ofR1123 and R125 in the sixth embodiment of the present invention. Inaddition, each of the computation conditions of FIGS. 26 and 27 issimilar to those of FIGS. 24 and 25.

As illustrated in FIGS. 26 and 27, by mixing R125 at a ratio of 30% byweight to 60% by weight with R1123, comparing with R410A, it isascertained that a refrigeration performance increases by 96% to 110%,and the cycle efficiency (COP) is 94 to 97%.

In particular, by mixing R125 at a ratio of 40% by weight to 50% byweight with R1123, since disproportionation of R1123 can be preventedand the discharge temperature can be lowered, a design of the equipmentwhen the high-load operation is performed and when freezing andrefrigerating are performed for increasing the discharge temperaturebecomes easy. Furthermore, the global warming potential can be reducedto 50 to 100% of R410A.

As described above, in a two-component system of R1123 and R125, whencomprehensively considering prevention of disproportionation, reductionof flammability, a performance when the cooling operation is performedand when the heating operation is performed, COP, and the dischargetemperature (that is, when specifying the proportions employed in theair conditioner which uses scroll compressor 1200 that will be describedlater), a mixture containing R125 at a ratio of 30% by weight to 60% byweight is desirable. More desirably, a mixture containing R125 at aratio of 40% by weight to 50% by weight is desirable.

Modification Example 2 of Working Fluid

In addition, the working fluid sealed in the refrigeration cycle deviceof the embodiment may be a three-component mixed working fluid made of(1) R1123 (1,1,2-trifluoroethylene), (2) R32 (difluoromethane), and (3)R125 (tetrafluoroethane). In particular, the working fluid is a mixedworking fluid in which the proportions of R32 and R125 is equal to orgreater than 30% and less than 60% by weight, and the proportions ofR1123 is equal to or greater than 40% by weight and less than 70% byweight.

In a case of employment to the scroll compressor 1200 which willdescribed later, by making proportions of R32 and R125 be equal to orgreater than 30% by weight, it is possible to suppress adisproportionation reaction of R1123. In addition, as proportions of R32and R125 increases, it is possible to further suppress adisproportionation reaction. In addition, R125 can reduce flammabilityof R1123.

FIGS. 28 and 29 are views comparing R410A and R1123 with each other bycomputing a refrigeration performance in a case where a pressure and atemperature in the refrigeration cycle, and a displacement volume of thecompressor are the same, and cycle efficiency (COP), in a case whereproportions of each of R32 and R125 is fixed to 50% by weight, and R32and R125 are mixed with R1123 in the sixth embodiment of the presentinvention. In addition, each of the computation conditions of FIGS. 28and 29 is similar to those of FIGS. 24 and 25.

As illustrated in FIGS. 28 and 29, by making proportions of each of R32and R125 30% by weight to 60% by weight, comparing with R410A, it isascertained that a refrigeration performance becomes 107 to 116%, andthe cycle efficiency (COP) is 93 to 96%.

In particular, by making proportions of R32 and R125 40% by weight to50% by weight, disproportionation can be prevented, the dischargetemperature can be lowered, and flammability can be reduced.Furthermore, the global warming potential can be reduced to 60 to 30% ofR410A.

In addition, in <Modification Example 2 of Working Fluid>, it isdescribed that proportions of each of R32 and R125 of three-componentworking fluid is made to be 50% by weight, but proportions of R32 may be0% by weight to 100% by weight, and proportions of R32 may be raised ina case where the refrigeration performance is desired to be improved. Onthe contrary, when reducing proportions of R32 and increasingproportions of R125, the discharge temperature can be lowered, andadditionally, flammability can be reduced.

As described above, in a three-component system of R1123, R32, and R125,when comprehensively considering prevention of disproportionation,reduction of flammability, a performance when the cooling operation isperformed and when the heating operation is performed, COP, and thedischarge temperature (that is, when specifying the proportions employedin the air conditioner which uses scroll compressor 1200 that will bedescribed later), a mixture in which R32 and R125 are mixed and a sum ofR32 and R125 is 30% by weight to 60% by weight is desirable. Moredesirably, a mixture in which a sum of R32 and R125 is 40% by weight to50% by weight is desirable.

Next, a configuration of scroll compressor 1200 which is an example ofcompressor 161 according to the embodiment will be described.

FIG. 30 is a longitudinal sectional view of scroll compressor 1200according to the sixth embodiment of the present invention, and FIG. 31is a sectional view in which main portions of compression mechanismportion 202 of the same scroll compressor 1200. Hereinafter, theconfiguration, the operation, and the action of scroll compressor 1200will be described.

As illustrated in FIG. 30, scroll compressor 1200 of the sixthembodiment of the present invention includes airtight container 201,compression mechanism portion 202 in the inside thereof, motor portion203, and oil storage portion 120.

By using FIG. 31, compression mechanism portion 202 will be described indetail. Compression mechanism portion 202 includes main bearing member211 which is fixed to the inside of airtight container 201 by welding orshrink-fitting, and has shaft 204. In addition, compression mechanismportion 202 is configured as revolving scroll 213 which meshes withfixed scroll 212 is interposed between fixed scroll 212 bolted on mainbearing member 211 and main bearing member 211. Fixed scroll 212 andrevolving scroll 213 respectively have a structure in which a spiral laprises (protrudes) from an end plate.

Between revolving scroll 213 and main bearing member 211, rotationrestraining mechanism 214 using an Oldham ring or the like, which guidesrevolving scroll 213 to be operated following a circular orbit bypreventing rotation of revolving scroll 213, is provided. It is possibleto operate the revolving scroll 213 following a circular orbit byeccentrically driving the revolving scroll 213 using eccentric shaftportion 204 a which is at an upper end of shaft 204.

Accordingly, compression chamber 215 which is formed between fixedscroll 212 and revolving scroll 213 performs compression aftersuctioning and confining the working refrigerant in compression chamber215 via suction pipe 216 which passes through the outside of airtightcontainer 201 and suction port 217 of an outer circumferential portionof fixed scroll 212 by moving the working fluid toward a center portionfrom an outer circumferential side while contracting an interval volume.The working fluid of which a pressure reaches a predetermined pressureis discharged to discharge chamber 122 by pushing and opening reed valve219 from discharge hole 218 formed at the center portion of fixed scroll212.

Discharge chamber 122 is a space which is provided on the end platesurface of fixed scroll 212 to cover discharge hole 218, and is formedby muffler 124. The working refrigerant discharged to discharge chamber122 is discharged to the inside of airtight container 201 via acommunication path provided in compression mechanism portion 202.Working refrigerant discharged to the inside of airtight container 201is discharged to refrigeration cycle device 1100 from airtight container201 via discharge pipe 123.

In addition, in order to avoid damage due to excessive deformation ofreed valve 219, valve stop 121 which suppresses a lift amount isprovided. In addition, reed valve 219 is provided, for example, on anend plate surface at a position at which discharge hole 218 of the endplate of fixed scroll 212 is formed.

FIG. 32 is a view illustrating a state where revolving scroll 213 mesheswith fixed scroll 212 in the sixth embodiment of the present invention.A left side of FIG. 32 is a view illustrating a state where the firstcompression chamber contains the working fluid, and a right side of FIG.32 is a view illustrating a state where the second compression chambercontains the working fluid.

As illustrated in FIG. 32, in compression chamber 215 which is formed byfixed scroll 212 and the revolving scroll 213, first compression chamber215 a formed on a lap outer wall side of revolving scroll 213 and secondcompression chamber 215 b which is formed on a lap inner wall side, arepresent. A suction volume of first compression chamber 215 a is greaterthan a suction volume of second compression chamber 215 b. In otherwords, since the timing at which the working fluid is contained varies,a corresponding pressure of first compression chamber 215 a and apressure of second compression chamber 215 b also vary.

FIG. 33 is a view illustrating a pressure rise curve of firstcompression chamber 215 a and second compression chamber 215 b in thesixth embodiment of the present invention.

Originally, in first compression chamber 215 a and second compressionchamber 215 b, since the timing of containment varies, a starting pointof the pressure curve does not match. However, here, in order to makethe difference apparent, a graph which matches the timings ofcontainment is used in the description. As illustrated in FIG. 33, it isascertained that a rate of pressure change of second compression chamber215 b having a small suction volume is greater than that of firstcompression chamber 215 a. In other words, pressure difference ΔPbbetween second compression chamber 215 b-1 which is formed one before,and second compression chamber 215 b-0 which is formed next, becomesgreater than pressure difference ΔPa of the same first compressionchamber 215 a, regarding second compression chamber 215 b, the workingfluid is likely to leak via a contact portion in the radial direction ofthe lap.

Returning to FIG. 30, pump 125 is provided at one end of shaft 204, andthe suction portion of pump 125 is disposed to be present in oil storageportion 120. Since pump 125 is driven at the same time with scrollcompressor 1200, it is possible to reliably suction up compressorlubricating oil 206 (oil, refrigerator oil) in oil storage portion 120provided on the bottom portion of airtight container 201 regardless ofthe pressure condition and the operation speed, and a concern aboutshortage of oil is solved.

Compressor lubricating oil 206 which is suctioned up by pump 125 issupplied to compression mechanism portion 202 through oil supply hole126 (refer to FIG. 31) which penetrates the inside of shaft 204. Inaddition, before compressor lubricating oil 206 is suctioned up by pump125, or after compressor lubricating oil 206 is suctioned up, byremoving foreign materials by an oil filter or the like, it is possibleto prevent the foreign materials from being incorporated intocompression mechanism portion 202, and further, to improve thereliability.

Compressor lubricating oil 206 guided to compression mechanism portion202 also becomes a backpressure source with respect to revolving scroll213, which has a pressure having substantially equivalent to thedischarge pressure of scroll compressor 1200. Accordingly, revolvingscroll 213 stably achieves a predetermined compression performancewithout being separated from or abuts against fixed scroll 212 beingbiased. Furthermore, by the supply pressure and the self-weight, a partof the compressor lubricating oil 206 infiltrates into a fitting portionbetween eccentric shaft portion 204 a and revolving scroll 213, and intobearing portion 166 between shaft 204 and main bearing member 211, byobtaining a means of escape, and after each part is lubricated, the partof compressor lubricating oil 206 is dropped and returns to oil storageportion 120.

In addition, regarding a position at which the working fluid iscontained in first compression chamber 215 a and second compressionchamber 215 b, as illustrated by a broken line (a curve of a finishedwinding of the fixed scroll of a symmetrical spring) of FIG. 32 in ageneral symmetrical scroll, a spiral finished winding portion of fixedscroll 212 release to the outside, and revolving scroll 213 is formednot to have a contact point. In this case, a containing position offirst compression chamber 215 a becomes a T point (non-symmetricaltaking-in position) on the left side of FIG. 32, the working fluid isheated on a route which reaches the T point, and since the stability ofR1123 is low compared to the refrigerant of the related art, such asR410A, there is a concern that a disproportionation reaction occursaccording to polymerization reaction and large amount of heat emitted.

Here, in the embodiment, a spiral lap is configured so that a positionat which the working fluid is confined in first compression chamber 215a and in second compression chamber 215 b is shifted by substantially180 degrees. Specifically, in a state where fixed scroll 212 andrevolving scroll 213 mesh with each other, the spiral lap of fixedscroll 212 extends to an extent equivalent to the spiral lap ofrevolving scroll 213. In this case, the position at which firstcompression chamber 215 a confines the working fluid becomes an S point(non-symmetrical taking-in position) on the left side of FIG. 32, andafter the working fluid is confined in first compression chamber 215 a,the rotation of shaft 204 advances by approximately 180 degrees, andthen, the second compression chamber 215 b confines the working fluid.Accordingly, it is possible to minimize the influence of increase inrefrigerant temperature caused by suctioning and heating, and further,to ensure the maximum suction volume with respect to first compressionchamber 215 a. In other words, it is possible to set a lap height to below, and as a result, since it is possible to reduce a void (=section ofleakage) of the contact portion in the radial direction of the lap, itis possible to further reduce leakage loss.

In addition, as illustrated in FIG. 31, on rear surface 213 e ofrevolving scroll 213, high-pressure region 230 and backpressure chamber129 which is set to have an intermediate pressure which is between ahigh pressure and a low pressure, are formed, and a plurality of oilsupply paths are provided, and at a part or in all of the oil supplypaths are configured to pass via backpressure chamber 129. By adding apressure from rear surface 213 e, revolving scroll 213 is stably pressedto fixed scroll 212, the leakage to compression chamber 215 frombackpressure chamber 129 is reduced, and a stable operation can beperformed.

Furthermore, by providing the plurality of oil supply paths, it ispossible to supply oil only by a necessary amount to a necessarylocation. For example, in a suction stroke before confining compressionchamber 215, a certain degree of seal oil is required, suctioning andoverheating of working fluid occur when a large amount oil is supplied,and volumetric efficiency deteriorates. In addition, similar to that inthe middle of compression, when the oil is massively supplied, an inputincreases due to viscosity loss. Here, it is ideal to supply the oilonly by a necessary amount to each location, and in order to realizethis, the plurality of oil supply paths are formed. In addition, bysupplying the oil via backpressure chamber 129, it is possible to reducethe pressure difference between the oil supply path and compressionchamber 215 to which the oil is supplied. For example, while in themiddle of suction stroke or compression, since the pressure differencein a case where the oil is supplied from backpressure chamber 129 set tohave an intermediate pressure is lower than that in a case where the oilis directly supplied from high-pressure region 230, it is possible tosupply an extremely small amount of oil which is a necessary minimumlimit. In this manner, it is possible to prevent excessive supply ofoil, and it is possible to suppress deterioration of performance causedby suctioning and heating, and an increase in input caused by viscosityloss.

In addition, by disposing seal member 178 on rear surface 213 e ofrevolving scroll 213, an inner side of seal member 178 is defined ashigh-pressure region 230, and an outer side of seal member 178 isdefined as backpressure chamber 129. In addition, at least one oilsupply path is configured of backpressure chamber oil supply path 151from high-pressure region 230 to backpressure chamber 129, andcompression chamber oil supply path 152 from backpressure chamber 129 tosecond compression chamber 215 b. In this manner, since it is possibleto completely separate a pressure of high-pressure region 230 and apressure of backpressure chamber 129 from each other by using sealmember 178, it is possible to stably control a pressure load from rearsurface 213 e of revolving scroll 213.

In addition, by providing backpressure chamber oil supply path 151 fromhigh-pressure region 230 to backpressure chamber 129, it is possible tosupply compressor lubricating oil 206 to a sliding portion of rotationrestraining mechanism 214 and a thrust sliding portion of fixed scroll212 and revolving scroll 213. In addition, by providing compressionchamber oil supply path 152 from backpressure chamber 129 to secondcompression chamber 215 b, it is possible to actively increase an amountof oil supplied to second compression chamber 215 b, and to suppressleakage loss in second compression chamber 215 b.

In addition, one opening end 151 b of backpressure chamber oil supplypath 151 is formed on rear surface 213 e of revolving scroll 213,opening end 151 b comes and goes to the outside and the inside of sealmember 178, and the other opening end 151 a is always open tohigh-pressure region 230. Accordingly, the oil can be intermittentlysupplied.

FIG. 34 is a view illustrating a state where revolving scroll 213 mesheswith fixed scroll 212 and viewed from the rear surface of revolvingscroll 213, in the sixth embodiment of the present invention. Inaddition, four sections of FIG. 34 are views in which the phase isshifted by 90 degrees.

As illustrated in FIG. 34, by seal member 178, the rear surface regionof revolving scroll 213 is divided into high-pressure region 230 on theinner side, and backpressure chamber 129 on the outer side. In a state(II), since opening end 151 b is open to backpressure chamber 129 whichis on the outside of seal member 178, the oil is supplied. Meanwhile, instates (I), (III), and (IV), since opening end 151 b is open to theinner side of seal member 178, the oil is not supplied.

In other words, one opening end 151 b of backpressure chamber oil supplypath 151 comes and goes to high-pressure region 230 and backpressurechamber 129 to each other, but only when the pressure difference isgenerated in both of opening ends 151 a and 151 b of backpressurechamber oil supply path 151, compressor lubricating oil 206 is suppliedto backpressure chamber 129. By this configuration, since the amount ofoil supplied can be adjusted by a ratio by which opening end 151 b comesand goes (across) seal member 178, it is possible to configure a passagediameter of backpressure chamber oil supply path 151 by a dimensionwhich is ten times greater than that of oil filter.

Accordingly, a concern that a foreign material is engaged with thepassage and blocks the passage is solved. Accordingly, at the same timewhen applying a stabilized backpressure, it is possible to maintain anexcellent state of lubrication of the thrust sliding portion androtation restraining mechanism 214, and to provide scroll compressor1200 which realizes high efficiency and high reliability. In addition,in the embodiment, a case where opening end 151 a is always inhigh-pressure region 230, and opening end 151 b comes and goes tohigh-pressure region 230 and backpressure chamber 129, is described asan example. However, even in case where opening end 151 a comes and goesto high-pressure region 230 and backpressure chamber 129, and openingend 151 b is always in backpressure chamber 129, since a pressuredifference is generated between opening ends 151 a and 151 b, it ispossible to realize intermittent oil supply, and to achieve similareffects.

In a case where the addition of the pressure from rear surface 213 e ofrevolving scroll 213 is not sufficiently applied, there is a concernthat a tilting phenomenon in which revolving scroll 213 is separatedfrom fixed scroll 212 occurs. In the tilting phenomenon, since theworking fluid to compression chamber 215 before being confined leaksfrom backpressure chamber 129, volumetric efficiency deteriorates. Inorder to prevent this, it is necessary that backpressure chamber 129maintains a predetermined pressure. Here, compression chamber oil supplypath 152 is configured so that second compression chamber 215 b afterconfining the working fluid and backpressure chamber 129 communicatewith each other. Accordingly, since the pressure of backpressure chamber129 becomes a predetermined pressure which is higher than a suctionpressure, it is possible to prevent the tilting phenomenon, and torealize high efficiency. In addition, even when the tilting isgenerated, since it is possible to guide the pressure of secondcompression chamber 215 b to backpressure chamber 129, early return to anormal operation is possible.

In the embodiment, the suction volume of first compression chamber 215 aformed on the lap outer wall side of revolving scroll 213 is greaterthan the suction volume of second compression chamber 215 b formed onthe lap inner wall side of revolving scroll 213. Accordingly, since itis possible to configure to shorten the path until reaching theconfining position of first compression chamber 215 a, and to heat therefrigerant before starting compression, it is possible to suppress adisproportionation reaction of R1123.

In addition, in the compressor of the embodiment, as the compressorlubricating oil, the polyvinyl ether oil is used.

In addition, as an additive which is added to compressor lubricating oil206, it is possible to use an additive containing at least one type of aphosphate ester anti-wear agent and a phenolic antioxidant.

Specific examples of the phosphate ester anti-wear agent includetributylphosphate, tripentyl phosphate, trihexyl phosphate, triheptylphosphate, trioctyl phosphate, trinonyl phosphate, tridecyl phosphate,triundecyl phosphate, tridodecyl phosphate, tritridecyl phosphate,tritetradecyl phosphate, tripentadecyl phosphate, trihexadecylphosphate, triheptadecyl phosphate, trioctadecyl phosphate, trioleylphosphate, triphenyl phosphate, tricresyl phosphate, trixylenylphosphate, cresyl diphenyl phosphate, and diphenyl xylenyl phosphate. Ingeneral, by adding 0.1 to 3 wt % of the phosphate ester anti-wear agentinto the refrigerator oil, by effectively adsorbing the phosphate esteranti-wear agent to a front surface of a sliding portion, and by creatinga film having a small shearing force on a sliding surface, it ispossible to obtain an anti-wear effect.

According to this configuration, by a sliding improving effect caused bythe anti-wear agent, local heat generation of the sliding portion issuppressed, and accordingly, it is possible to obtain an effect ofsuppressing self-degradable reaction of the refrigerant R1123.

In addition, specific examples of a phenolic antioxidant include propylgallate, 2,4,5-trihydroxybutyrophenone, t-butylhydroquinone,nordihydroguaiaretic acid, butyl hydroxyanisole, 4-hydroxymethyl-2,6-di-t-butylphenol, octyl gallate, butylhydroxytoluene, and dodecylgallate. By adding 0.1 to 1 wt % of antioxidant to base oil, it ispossible to effectively captures the radicals, and to prevent thereaction. In addition, minimize coloring of the base oil itself due tothe antioxidant.

According to this configuration, as the phenolic antioxidant effectivelycaptures the radicals generated in the inside of airtight container 201,it is possible to obtain an effect of suppressing a disproportionationreaction of R1123.

In addition, limonene may be added in an amount of approximately 5% ofthe refrigerant amount of R1123 in order to prevent the reaction ofhighly reactive molecules containing a double bond and fluorine atomlike R1123. Scroll compressor 1200 of the embodiment and refrigerationcycle device 1100 which uses the same have a closed system, and asdescribed above, the lubricating oil is sealed as the base oil. Ingeneral, the viscosity of the lubricating oil which becomes the base oilsealed in scroll compressor 1200 is generally approximately 32 mm²/s to68 mm²/s. Meanwhile, the viscosity of limonene is very low which isapproximately 0.8 mm²/s. Therefore, the viscosity of the lubricating oilrapidly decreases to be 60 mm²/s in a case where approximately 5% oflimonene is mixed therein, 48 mm²/s in a case where 15% of limonene ismixed therein, and 32 mm²/s in a case where 35% of limonene is mixedtherein. Therefore, in order to prevent the reaction of R1123, when alarge amount of limonene is mixed therein, the reliability of scrollcompressor 1200 and refrigeration cycle device 1100 is influenced by thedecrease in viscosity of the lubricating oil, for example, wear due to alubricating defect and generation of metallic soap due to a contactstate of metal on the sliding surface.

Meanwhile, in order to compensate for the decrease in viscosity of thebase oil generated by mixing limonene having an amount appropriate forpreventing the reaction therein, by setting high-viscosity lubricatingoil as a base in advance, or by mixing super high-viscosity lubricatingoil having an amount which is equal to or greater than a mixing amountof limonene, the lubricating oil of scroll compressor 1200 of theembodiment ensures appropriate viscosity of the lubricating oil.

Specifically, when lubricating oil of which the viscosity is 78 mm²/s ina case where 5% of limonene is mixed therein, and lubricating oil ofwhich the viscosity is approximately 230 mm²/s in a case where 35% oflimonene is mixed therein, are selected, it is possible to ensure 68mm²/s in viscosity after the mixing. In addition, in order to maximizean effect of preventing the reaction of R1123 using limonene, an extremeexample, such as increase in the mixing amount of limonene to 70% or80%, is also considered. However, in this case, the viscosity of thehigh-viscosity lubricating oil which becomes the base becomes 8500 mm²/sor 25000 mm²/s, respectively, and exceeds 3200 mm²/s that is the maximumvalue of ISO standard. In addition, since it is also difficult touniform mix limonene therein, actual employment is difficult to beconsidered.

In addition, in a case where super-high viscosity lubricating oil ismixed with limonene by an amount equivalent to each other, by mixing 800mm²/s to 1000 mm²/s of lubricating oil with limonene, viscosity of 32mm²/s to 68 mm²/s is obtained. In addition, in a case where the limoneneand the super-high viscosity oil which have different viscosity aremixed with each other, when performing the mixing while adding thesuper-high viscosity oil to the limonene little by little, lubricatingoil of which composition viscosity is relatively uniform, can beobtained.

In addition, limonene is described as an example in the embodiment, butsimilar effects can also be obtained by a terpene type or a terpenoidtype. For example, it is possible to select hemiterpene type isoprene,prenol, 3-methyl butanoic acid and monoterpene type geranyl diphosphate,cineole, farnesyl diphosphate of pinene and sesquiterpene, artemisinin,bisabolol, diterpene type geranylgeranyl diphosphate, retinol, retinal,phytol, paclitaxel, forskolin, aphidicolin and triterpene type squalene,and lanosterol, in accordance with a use temperature of scrollcompressor 1200 and refrigeration cycle device 1100, and requiredviscosity of the lubricating oil.

In addition, the exemplified viscosity is a specific example in scrollcompressor 1200 having a high-pressure container, but in scrollcompressor 1200 which uses the lubricating oil having comparatively lowviscosity of 5 mm²/s to 32 mm²/s, and has a low-viscosity container,similar embodiment is also possible, and similar effects can beobtained.

In addition, the terpene type and the terpenoid type, such as limonene,has solubility with respect to plastic, but when limonene having anamount which is equal to or less than 30% is mixed therein, theinfluence thereof is small, and electric insulation required for plasticin scroll compressor 1200 does not have a problem. However, in a casewhere there is a problem, for example, in a case where the reliabilityis required for a long period of time, and in a case where a general usetemperature is high, it is desirable to use polyimide, polyimidoamide,or polyphenylene sulfide which has chemical resistant properties.

In addition, a winding wire of motor portion 203 of scroll compressor1200 of the embodiment, a conductor is coated with varnish(thermosetting insulating material) and baked with an insulating filmtherebetween. Examples of the thermosetting insulating material includea polyimide resin, an epoxy resin, and an unsaturated polyester resin.Among these, the polyimide resin can be obtained by coating in a stateof polyamic acid which is a precursor, and baking the polyamic acidapproximately at 300° C. to achieve polyimidation. It is known thatimide reaction occurs due to reaction between amine and carboxylic acidanhydride. Since there is a possibility that the refrigerant R1123 alsoreacts in a short circuit between electrodes, by coating a motor windingwith polyimidic acid varnish (polyimide precursor which can allowaromatic diamine and aromatic tetracarboxylic dianhydride to react is amain component), it is possible to prevent a short circuit betweenelectrodes.

Therefore, even in a state where a coil of motor portion 203 infiltratesinto a liquid refrigerant, it is possible to maintain high resistancebetween windings, to suppress discharge between windings, and to obtainan effect of suppressing self-degradable reaction of the refrigerantR1123.

FIG. 35 is a partial sectional view illustrating a structure in thevicinity of a power supply terminal of scroll compressor 1200 accordingto the sixth embodiment of the present invention.

In FIG. 35, power supply terminal 171, glass insulating material 172,metal lid body 173 which holds the power supply terminal, flag terminal174 which is connected to the power supply terminal, and lead wire 175,are illustrated. In scroll compressor 1200 according to the embodiment,a doughnut-like insulating member 176 which adheres to glass insulatingmaterial 172 which is an insulating member, is pipe-connected onto powersupply terminal 171 on an inner side of airtight container 201 of scrollcompressor 1200. As doughnut-like insulating member 176, a member whichmaintains insulation properties and has resistance against fluorinatedacid, is appropriate. For example, a ceramic insulator or a HNBR rubberdoughnut-like spacer is employed. It is mandatory that doughnut-likeinsulating member 176 adheres to glass insulating material 172, but itis preferable doughnut-like insulating member 176 also adheres to aconnection terminal.

In power supply terminal 171 configured in this manner, due todoughnut-like insulating member 176, a creeping distance on the powersupply terminal and an inner surface of scroll compressor 1200 of a lidbody becomes long, terminal tracking can be prevented, and ignitioncaused by discharge energy of R1123 can be prevented. In addition, it ispossible to prevent fluorinated acid generated by decomposing R1123 fromcorroding glass insulating material 172.

In addition, scroll compressor 1200 of the embodiment may be a so-calledhigh-pressure shell type compressor in which discharge hole 218 is opento the inside of airtight container 201, and the inside of airtightcontainer 201 is filled with refrigerant compressed in compressionchamber 215. Meanwhile, scroll compressor 1200 may be a so-calledlow-pressure shell type scroll compressor 1200 in which suction hole 118is open to the inside of airtight container 201, and the inside ofairtight container 201 is filled with refrigerant which is before beingpressed in compression chamber 215. This case is desirable because thetemperature substantially decreases due to the introduction of alow-temperature refrigerant in compression chamber 215, and adisproportionation reaction of R1123 is suppressed, in a configurationin which a temperature is likely to increase until the refrigerant isheated in the inside of airtight container 201 and is introduced tocompression chamber 215.

In addition, in high-pressure shell type scroll compressor 1200, afterthe refrigerant discharged from discharge hole 218 passes through theperiphery of motor portion 203, and is heated by motor portion 203 inthe inside of airtight container 201, the refrigerant may be dischargedto the outside of airtight container 201 from discharge pipe 123. Thisconfiguration is desirable because a disproportionation reaction ofR1123 is suppressed since it is possible to decrease the temperature ofthe refrigerant in compression chamber 215, even when the temperature ofthe refrigerant discharged from discharge pipe 123 is equivalent.

Seventh Embodiment

Next, a seventh embodiment of the present invention will be described.

FIG. 36 is a view illustrating a configuration of a refrigeration cycledevice 1101 according to the seventh embodiment of the presentinvention.

Refrigeration cycle device 1101 of the embodiment is connected tocompressor 1102, condenser 1103, expansion valve 1104 which is athrottle mechanism, and evaporator 1105 in order by refrigerant piping1106, and a refrigeration cycle circuit is configured. In therefrigeration cycle circuit, the working fluid (refrigerant) is sealed.

Next, a configuration of refrigeration cycle device 1101 will bedescribed.

As condenser 1103 and evaporator 1105, in a case where a surroundingmedium is air, a fin and tube type heat exchanger or a parallel flowtype (micro tube type) heat exchanger are used.

Meanwhile, as condenser 1103 and evaporator 1105 in a case where thesurrounding medium is brine or a refrigerant of two-dimensional typerefrigeration cycle device, a double pipe heat exchanger, a plate typeheat exchanger, or a shell and tube type heat exchanger, are used.

As expansion valve 1104, for example, an electronic expansion valvewhich uses a pulse motor driving method, or the like is used.

In refrigeration cycle device 1101, in condenser 1103, fluid machinery1107 a which is a first transporting portion and drives (flows) thesurrounding medium (first medium) which exchanges heat with therefrigerant to a heat exchanging surface of condenser 1103, isinstalled. In addition, in evaporator 1105, fluid machinery 1107 b whichis a second transporting portion and drives (flows) the surroundingmedium (second medium) which exchanges heat with the refrigerant to aheat exchanging surface of evaporator 1105, is installed. In addition,flow path 1116 of the surrounding medium is provided in each of thesurrounding mediums.

Here, as the surrounding medium, when the air in the atmosphere is used,there is a case where water or brine, such as ethylene glycol, is used.In addition, in a case where refrigeration cycle device 1101 is thetwo-dimensional type refrigeration cycle device, a refrigerant which ispreferable for the refrigeration cycle circuit and a working temperatureregion, for example, hydrofluorocarbons (HFC), hydrocarbons (HC), orcarbon dioxide, is used.

As fluid machineries 1107 a and 1107 b which drive the surroundingmedium, in a case where the surrounding medium is air, an axial flowblower, such as a propeller fan, a cross flow fan, or a centrifugalblower, such as a turbo blower, is used, and in a case where thesurrounding medium is brine, a centrifugal pump is used. In addition, ina case where refrigeration cycle device 1101 is a two-dimensional typerefrigeration cycle device, as fluid machineries 1107 a and 1107 b fortransporting the surrounding medium, compressor 1102 plays a rolethereof.

In condenser 1103, at a location (hereinafter, in the specification,referred to as “two-phase pipe of condenser”) at which the refrigerantthat flows in the inside thereof flows in two phases (a state where gasand liquid are mixed with each other), condensation temperaturedetecting portion 1110 a is installed, and it is possible to measure thetemperature of the refrigerant.

In addition, between an outlet of condenser 1103 and an inlet ofexpansion valve 1104, condenser outlet temperature detecting portion1110 b is installed. Condenser outlet temperature detecting portion 1110b can detect overcooling degree (a value obtained by subtracting thetemperature of condenser 1103 from an inlet temperature of expansionvalve 1104) of inlet of expansion valve 1104.

In evaporator 1105, at a location (hereinafter, in the specification,referred to as “two-phase pipe of evaporator”) at which the refrigerantthat flows in the inside thereof flows in two phases, evaporationtemperature detecting portion 1110 c is provided, and it is possible tomeasure the temperature of the refrigerant in the inside of evaporator1105.

In a suction portion (between an outlet of evaporator 1105 and an inletof compressor 1102) of compressor 1102, suction temperature detectingportion 1110 d is provided. Accordingly, it is possible to measure thetemperature (suction temperature) of the refrigerant suctioned tocompressor 1102.

In a case where, for example, an electronic thermostat which isconnected to the working fluid in a contact state at the piping in whichthe refrigerant flows or an outer pipe of a heat transfer pipe is usedas each of the above-described temperature detecting portion, there isalso a case where a sheath pipe type electronic thermostat whichdirectly comes into contact with the working fluid, is used.

Between the outlet of condenser 1103 and the inlet of expansion valve1104, high-pressure side pressure detecting portion 1115 a which detectsa pressure on a high pressure side (a region in which the refrigerantfrom the outlet of compressor 1102 to the inlet of expansion valve 1104is present at a high pressure) of the refrigeration cycle circuit, isinstalled.

At the outlet of expansion valve 1104, low-pressure side pressuredetecting portion 1115 b which detects a pressure on a low pressure side(a region in which the refrigerant from the outlet of expansion valve1104 to the inlet of compressor 1102 is present at a low pressure) ofthe refrigeration cycle circuit, is installed.

As high-pressure side pressure detecting portion 1115 a and low-pressureside pressure detecting portion 1115 b, for example, a member whichconverts displacement of a diaphragm into an electric signal, or thelike is used. In addition, instead of high-pressure side pressuredetecting portion 1115 a and low-pressure side pressure detectingportion 1115 b, a differential pressure gauge (measuring means formeasuring a pressure difference between the outlet and the inlet ofexpansion valve 1104), may be used.

In addition, in the above-described description of the configuration, anexample in which refrigeration cycle device 1101 is provided with all ofeach temperature detecting portion and each pressure detecting portion,is described, but in control which will be described later, a detectingportion which does not use a detected value can be omitted.

Next, a control method of refrigeration cycle device 1101 will bedescribed. First, control when a general operation is performed will bedescribed.

When a general operation is performed, the overheating degree of theworking fluid at the suction portion of compressor 1102, which is atemperature difference between suction temperature detecting portion 110d and evaporation temperature detecting portion 110 c, is computed. Inaddition, expansion valve 1104 is controlled so that the overheatingdegree becomes a target overheating degree (for example, 5K) determinedin advance.

In addition, at a discharge portion of compressor 1102, a dischargetemperature detecting portion (not illustrated) is further provided, andit is possible to perform the control by using the detected vale. Inthis case, the overheating degree of the working fluid at the dischargeportion of compressor 1102, which is a temperature difference betweenthe discharge temperature detecting portion and condensation temperaturedetecting portion 1110 a, is computed. In addition, expansion valve 1104is controlled so that the overheating degree becomes a targetoverheating degree determined in advance.

Next, control in a case where a possibility of occurrence of adisproportionation reaction increases, and a special operation state isachieved, will be described.

In the embodiment, in a case where a temperature detected value ofcondensation temperature detecting portion 1110 a becomes excessive,control of opening expansion valve 1104, and decreasing the pressure andthe temperature of the high-pressure side working fluid in the inside ofrefrigeration cycle device 1101, is performed.

In general, it is necessary to perform the control so that asupercritical condition which exceeds a critical point (a pointdescribed as T_(cri) in FIG. 37 which will be described later) is notachieved by the refrigerant excluding carbon dioxide. This is because,in a supercritical state, a material is placed in a state where eithergas or liquid is not present, and the behavior thereof is unstable andactive.

Here, in the embodiment, considering a temperature (criticaltemperature) at the critical point as one criterion, using thetemperature, an opening degree of expansion valve 1104 is controlled sothat the condensation temperature does not approach approximately avalue (5K) determined in advance. In addition, in a case where theworking fluid (mixed refrigerant) containing R1123 is used, by using thecritical temperature of the mixed refrigerant, the control is performedso that the temperature of the working fluid does not become equal to orgreater than the critical temperature (−5° C.).

FIG. 37 is a Mollier diagram illustrating an operation of refrigerationcycle device 1101 in the seventh embodiment of the present invention. InFIG. 37, isotherm 1108 and saturation liquid line and saturation vaporline 1109 are illustrated.

In FIG. 37, a refrigeration cycle which is under an excessive pressurecondition which becomes a cause of occurrence of a disproportionationreaction, is illustrated by a solid line (EP), and a refrigeration cyclewhich is under a normal operation condition, is illustrated by a brokenline (NP).

If a temperature value in condensation temperature detecting portion1110 a provided in two-phase pipe of condenser 1103 is equal to or lessthan 5K (EP in FIG. 37) with respect to the critical temperature storedin a control device in advance, the control device controls the openingdegree of expansion valve 1104 to be high. As a result, similar to NP ofFIG. 37, since the condensation pressure which is on the high-pressureside of refrigeration cycle device 1101 decreases, it is possible tosuppress a disproportionation reaction which occurs due to an excessivepressure rise of the refrigerant, or to suppress the pressure rise evenin a case where a disproportionation reaction occurs.

In addition, the above-described control method is a method forcontrolling the opening degree of expansion valve 1104 by indirectlygrasping the pressure in the inside of condenser 1103 from thecondensation temperature measured by condensation temperature detectingportion 1110 a. The method is particularly preferable since it ispossible use the condensation temperature as a target instead of thecondensation pressure in a case where the working fluid containing R1123is azeotrope or pseudoazeotrope, and a temperature difference(temperature gradient) between a dew point and a boiling point of theworking fluid containing R1123 in condenser 1103, is zero or small.

Modification Example 1 of Control Method

In addition, as described above, by comparing the critical temperatureand the condensation temperature, by indirectly detecting a highpressure state (the pressure of the refrigerant in the inside ofcondenser 1103) of refrigeration cycle device 1101, instead of thecontrol method which commands an appropriate operation to expansionvalve 1104 or the like, based on the pressure which is directlymeasured, a method for controlling the opening degree of expansion valve1104 may be used.

FIG. 38 is a Mollier diagram illustrating a control operation ofModification Example 1 in the seventh embodiment of the presentinvention.

In FIG. 38, from the discharge portion of compressor 1102 to the inletsof condenser 1103 and expansion valve 1104, the refrigeration cycle in astate where an excessive pressure rise continues to be generated, isillustrated by a solid line (EP), and the refrigeration cycle in a statewhich is out of the above-described excessive-pressure state, isillustrated by a broken line (NP).

In the operation, in a case where a pressure difference obtained bysubtracting, for example, a pressure P_(cond) at the outlet of condenser1103 detected by high-pressure side pressure detecting portion 1115 afrom a pressure (critical pressure) P_(cri) at the critical point storedin the control device in advance, is smaller than a value (for example,Δp=0.4 MPa) determined in advance (EP of FIG. 38), from the dischargeport of compressor 102 to the inlet of expansion valve 1104, bydetermining that a disproportionation reaction occurs in the workingfluid containing R1123, or there is a concern about occurrence of adisproportionation reaction, the opening degree of expansion valve 1104is controlled to be high to avoid continuity under the high-pressurecondition.

As a result, as illustrated by NP in FIG. 38, the refrigeration cycle inFIG. 38 acts on the high pressure (compression pressure) to decrease,and it is possible to suppress the pressure rise that causes occurrenceof a disproportionation reaction and occurs after a disproportionationreaction.

In the working fluid containing R1123, it is preferable to use thecontrol method in a case of a non-azeotropic state, in particular, in acase where a temperature gradient is large in the condensation pressure.

Modification Example 2 of Control Method

In addition, instead of the control method using the above-describedcritical temperature or the critical pressure as a standard, a controlmethod based on the overcooling degree may be used.

FIG. 39 is a Mollier diagram illustrating a control operation ofModification Example 2 of a control method of refrigeration cycle device1101 in the seventh embodiment of the present invention.

In FIG. 39, the refrigeration cycle which is under an excessive pressurecondition which is a cause of occurrence of a disproportionationreaction, is considered as EP, and is illustrated by a solid line, andthe refrigeration cycle which is under a normal operation is consideredas NP, and is illustrated by a broken line.

In general, in refrigeration cycle device 1101, by appropriatelycontrolling the refrigeration cycle of expansion valve 1104 orcompressor 1102, and by making the size of the heat exchanger and therefrigerant filling amount appropriate, the temperature of therefrigerant in the inside of condenser 1103 is set so that thetemperature increases by a certain degree with respect to thesurrounding medium. In addition, in general, the overcooling degree is avalue which is approximately 5K. Even in the working fluid which issimilarly used in refrigeration cycle device 1101 and contains R1123,similar measures are taken.

In refrigeration cycle device 1101 in which the above-described measureis taken, if the pressure of refrigerant is excessively high, there isalso a tendency for the overcooling degree of the inlet of expansionvalve 1104 to increase as illustrated by EP of FIG. 39. In addition, inthe embodiment, considering the overcooling degree of the refrigerant ofthe inlet of expansion valve 1104 as a standard, the opening degree ofexpansion valve 1104 is controlled.

In addition, in the embodiment, considering the overcooling degree ofthe refrigerant at the inlet of expansion valve 1104 when the normaloperation is performed as 5K, using 15K which is three times the valueas a criterion, the opening degree of expansion valve 1104 iscontrolled. The overcooling degree which is a threshold value is threetimes the value, because there is a possibility that the overcoolingdegree changes within the range according to the operation condition.

Specifically, first, the overcooling degree is calculated from thedetected value of condensation temperature detecting portion 1110 a andthe detected value of condenser outlet temperature detecting portion1110 b. The overcooling degree is a value obtained by subtracting thedetected value of condenser outlet temperature detecting portion 1110 bfrom the detected value of condensation temperature detecting portion1110 a. In addition, when the overcooling degree at the inlet ofexpansion valve 1104 reaches the value (15K) determined in advance, anoperation of controlling the opening degree of expansion valve 1104 tobe high is performed, and the condensation pressure at a high-pressurepart of refrigeration cycle device 1101 is controlled to decrease (froma solid line to a broken line of FIG. 39).

Since the decrease in condensation pressure is the same as the decreasein condensation temperature, the condensation temperature decreases fromT_(cond1) to T_(cond2), and the overcooling degree at the inlet ofexpansion valve 1104 decreases from T_(cond1)−T_(exin) toT_(cond2)−T_(exin) (here, a working fluid temperature of the inlet ofexpansion valve 1104 does not change, and is T_(exin)). As describedabove, since the overcooling degree also decreases according to thedecrease in condensation pressure in the inside of refrigeration cycledevice 1101, it is ascertained that the control in condensation pressurein the inside of refrigeration cycle device 1101 even in a case wherethe overcooling degree is considered as a standard.

FIG. 40 is a view illustrating piping joint 1117 which configures a partof piping of refrigeration cycle device 1101 of the seventh embodimentof the present invention.

In a case where refrigeration cycle device 1101 of the present inventionis used, for example, in home spilt type air conditioner (airconditioner), the refrigeration cycle device 1101 is configured of anoutdoor unit including an outdoor heat exchanger and an indoor unitincluding an indoor heat exchange. The outdoor unit and the indoor unitcannot be integrated with each other in the configuration. Accordingly,by using a mechanical joint which is illustrated in FIG. 40 similar tounion flare 1111, the outdoor unit and the indoor unit are connected toeach other at an installation location.

If a connection state of the mechanical joint deteriorates due to acause when the work is not sufficient, or the like, the refrigerantleaks from the joint part, and this causes the negative influence on theequipment performance. In addition, since the working fluid containingR1123 itself is greenhouse gas having a greenhouse effect, there is alsoa concern about a negative influence on global environment. Accordingly,the refrigerant leakage is rapidly detected and repaired.

Examples of a method for detecting the refrigerant leakage include amethod of coating the part with a detection agent, and detecting whetheror not bubbles are generated, and a method of using a detection sensor,but it takes time and effort in each method.

Here, in the embodiment, by winding seal 1112 containing apolymerization promoter on an outer circumference of union flare 1111,the detection of refrigerant leakage becomes easy, and reduction ofleakage amount is achieved.

Specifically, in the working fluid containing R1123, when polymerizationreaction occurs, generation of polytetrafluoroethylene which is one of afluorinated carbon resin is used. Specifically, by intentionallybringing the working fluid containing R1123 and polymerization promoterinto contact with each other at the location of leakage, at the locationof leakage, polytetrafluoroethylene is configured to be extracted andsolidified. As a result, since the leakage is likely to be detectedeasily and visually, it is possible to shorten the time which is takenfor finding the leakage and performing the repair.

Furthermore, since a part at which polytetrafluoroethylene is generatedis a part of leakage of the working fluid containing R1123,spontaneously, since a polymerization product is generated and adheresto a part at which the leakage is prevented, it is also possible toreduce the leakage amount.

Eighth Embodiment

Next, an eighth embodiment of the present invention will be described.

FIG. 41 is a view illustrating a configuration of refrigeration cycledevice 1130 according to the eighth embodiment of the present invention.

Refrigeration cycle device 1130 illustrated in FIG. 41 and refrigerationcycle device 1101 of the seventh embodiment, are different from eachother in that bypass pipe 1113 provided with an opening and closingvalve, and is connected to the inlet and the outlet of expansion valve1104 is newly installed. In addition, refrigeration cycle device 1130and refrigeration cycle device 1101 are also different from each otherin that a purge line having relief valve 1114 is provided between theoutlet of condenser 1103 and the inlet of expansion valve 1104. Theopening side of relief valve 1114 is disposed outdoor. In addition, inFIG. 41, description of each temperature detecting portion and eachpressure detecting portion which are described by using FIG. 36, isomitted.

By performing a control method (for example, a control method forcontrolling the opening degree of expansion valve 1104 so that a valueobtained by subtracting the working fluid temperature measured by thetwo-phase tube of condenser 1103 from the critical temperature of theworking fluid containing R1123 is equal to or greater than 5K, or acontrol method for performing the control so that a difference betweenthe critical pressure of the working fluid and the pressure detected byhigh-pressure side pressure detecting portion 1115 a is equal to orgreater than 0.4 MPa) described in the seventh embodiment, even in acase where the opening degree of expansion valve 1104 is high, there isa possibility that a case where the decrease in pressure is notimproved, or a situation in which a speed of decrease in pressure isdesired to be raised, occur.

Here, in a case where the above-described situation is generated, byopening the opening and closing valve provided in bypass pipe 1113 ofthe embodiment, and by allowing the refrigerant to flow to bypass pipe1113, the pressure of the working fluid on a high pressure side rapidlydecreases and it is possible to suppress damage of refrigeration cycledevice 1130.

Furthermore, in addition to the control of increasing the opening degreeof expansion valve 1104, and the control of the opening and closingvalve provided in bypass pipe 1113, the control is more preferable sincedamage of refrigeration cycle device 1130 is prevented if compressor1102 is emergency-stopped. In addition, in a case where compressor 1102is emergency-stopped, it is preferable not to stop fluid machineries1107 a and 1107 b since the pressure of the working fluid on thehigh-pressure side rapidly decreases.

Even in a case where the above-described response is performed, a casewhere a disproportionation reaction is not suppressed, specifically, acase where a difference between the critical temperature of the workingfluid and the condensation temperature detected by condensationtemperature detecting portion 1110 a is less than 5K, or a case where adifference between the critical pressure of the working fluid and thepressure detected by high-pressure side pressure detecting portion 1115a is less than 0.4 MPa, are assumed. In this case, since there is aconcern that the pressure of the refrigerant in the inside ofrefrigeration cycle device 1130 increases, a necessity of releasing therefrigerant of which the pressure is high to the outside, and preventingdamage of refrigeration cycle device 1130, is generated. Here, reliefvalve 1114 which purges the working fluid containing R1123 in the insideof refrigeration cycle device 1130 to an outer space, is controlled toopen.

Here, it is preferable that an installation position of relief valve1114 in refrigeration cycle device 1130 is on a high-pressure side.Furthermore, it is particularly preferable that relief valve 1114 isinstalled from the outlet of condenser 1103 illustrated in theembodiment to the inlet of expansion valve 1104 (at this position, sincethe working fluid is in a high-pressure overcooling liquid state, awater hammering action which causes a result of rapid pressure riseaccording to a disproportionation reaction is likely to occur), orrelief valve 1114 is installed from the discharge portion of compressor1102 to the inlet of condenser 1103 (at this position, since the workingfluid is present in a high-temperature and high-pressure gas state, amolecular motion becomes active, and a disproportionation reaction islikely to occur).

Relief valve 1114 is provided on the outdoor unit side. In this case,the aspect is called an aspect which is considered not to directlyinfluence a human and commodity, since a configuration in which theworking fluid is not emitted to a residential space on the indoor sidein a case of the air conditioner, and the working fluid is not emittedto a product display side, such as a showcase, in a case of a freezingand refrigeration unit, is possible.

In addition, it is preferable to turn off a power source, for example,to open relief valve 1114 and stop refrigeration cycle device 1130, fromthe viewpoint of safety.

Ninth Embodiment

Next, a ninth embodiment of the present invention will be described.

FIG. 42 is a view illustrating a configuration of refrigeration cycledevice 1140 according to the ninth embodiment of the present invention.

Refrigeration cycle device 1140 illustrated in FIG. 42 and refrigerationcycle device 1101 of the seventh embodiment are different from eachother in that first medium temperature detecting portion 1110 e whichdetects the temperature of the first medium before flowing intocondenser 1103, and second medium temperature detecting portion 1110 fwhich detects the temperature of the second medium before flowing intoevaporator 1105, are provided. Furthermore, the detected values of eachtemperature detecting portion and each pressure detecting portion, andinput power of compressor 1102 and fluid machineries 1107 a and 1107 b,are stored in an electronic storage device (not illustrated) for acertain period of time.

FIG. 43 is a view illustrating an operation of refrigeration cycledevice 1140 of the ninth embodiment of the present invention in aMollier diagram.

In FIG. 43, the refrigeration cycle illustrated by EP is thecondensation pressure when a disproportionation reaction occurs, and therefrigeration cycle illustrated by NP indicates the refrigeration cyclewhen the normal operation is performed. In addition, in FIG. 43, inorder to make the description simple, a cycle change (example: adifference in evaporation pressures between NP and EP) when thecondensation pressure increases is not described.

As a reason of a rapid increase in the condensation temperature of theworking fluid containing R1123 which is measured in the two-phase pipein the inside of condenser 1103, (1) a rapid increase in surroundingmedium temperatures T_(mcon) and T_(meva), (2) a pressure rise actiondue to an increase in power of compressor 1102, and (3) a change in flow(a change in power of any of fluid machineries 1107 a and 1107 b whichdrives the surrounding medium) of the surrounding medium, areconsidered. In addition, as a specific phenomenon of the working fluidcontaining R1123, (4) a pressure rise action due to a disproportionationreaction is employed. Here, in the embodiment, in order to specify thata disproportionation reaction occurs of (4), the control is performedafter determining that phenomenon of (1) to (3) does not occur.

Here, in the control method of the embodiment, in a case where an amountof change in the condensation temperature of the working fluidcontaining R1123 with respect to an amount of change in temperature orinput power of (1) to (3), expansion valve 1104 is controlled to open.

Hereinafter, a specific control method will be described. First, sinceit is difficult to compare the amount of change in temperature and theamount of change in input power value with each other under the samestandard, when measuring the amount of change in temperature, the inputpower is controlled not to change. In other words, when measuring theamount of change in temperature, a motor rotation speed of compressor1102 and fluid machineries 1107 a and 1107 b are maintained to beconstant.

For example, the amount of change in temperature is measured at acertain time interval, for example, for 10 seconds to 1 minute. Beforethe measurement, for example, approximately 10 seconds to 1 minute ago,the amount of input power of compressor 1102 and fluid machineries 1107a and 1107 b is controlled to be maintained to a certain value. At thistime, an amount of change per unit time of the amount of input power ofcompressor 1102 and fluid machineries 1107 a and 1107 b substantiallybecomes zero. Here, the amount is “substantially” zero because a changein a suctioned state of compressor 1102 due to deviation of refrigerantin compressor 1102, or a slight change in input power due to influenceof blowing of wind or the like in a case where the first medium and thesecond medium are surrounding air in fluid machineries 1107 a and 1107b, are generated. In other words, the “substantially zero” means thatthe amount of change includes a slight behavior and is smaller than apredetermined value determined in advance.

Under the above-described condition, in a case where the amount ofchange per unit time of the condensation temperature measured bycondensation temperature detecting portion 1110 a is greater than any ofthe amount of change per unit time of the temperature of the firstmedium detected by first medium temperature detecting portion 1110 e,and the amount of change per unit time of the temperature of the secondmedium detected by second medium temperature detecting portion 110 f, itis considered that a disproportionation reaction occurs, expansion valve1104 is controlled to open.

In addition, only in controlling the opening degree of expansion valve1104, to be prepared for a case where the pressure rise generatedaccording to a disproportionation reaction cannot be controlled, similarto the eighth embodiment, bypass pipe 1113 may be provided in parallelwith expansion valve 1104, compressor 1102 may be emergency-stopped, andfurther, means, such as relief valve 1114, which reduces the pressure byemitting the refrigerant to the outside may be provided.

In addition, in the embodiment, a control example of expansion valve1104 in which control is performed considering the amount of change ofthe temperature detecting portion installed in the two-phase pipe ofcondenser 1103 as a standard, but an amount of change in pressure at anypoint from the discharge portion of compressor 1102 to the inlet ofexpansion valve 1104 may be considered as a standard, and an amount ofchange in overcooling degree of the inlet of expansion valve 1104 may beconsidered as a standard.

In addition, using the embodiment being combined with any of theabove-described seventh embodiment or the eighth embodiment, ispreferable since it is possible to further improve the reliability.

Tenth Embodiment

Next, a tenth embodiment of the present invention will be described.

FIG. 44 is a sectional view of scroll compressor 1200 according to atenth embodiment of the present invention.

Since the embodiment is the same as the sixth embodiment except thepresence and absence of reed valve 219 provided in discharge hole 218,description of configurations other than this will be omitted.

In the sixth embodiment, discharge hole 218 is provided in reed valve219 (check valve), but in the embodiment, reed valve 219 is not providedin discharge hole 218. Therefore, discharge chamber 122 alwayscommunicates with compression chamber 215 in the vicinity thereof viadischarge hole 218, and discharge chamber 122 and compression chamber215 are placed in a substantially same pressure state. In addition, inthe embodiment, since reed valve 219 is not provided in discharge hole218, valve stop 121 is also not provided, either.

Since a condition in which a disproportionation reaction is particularlylikely to occur is a condition under an excessive high temperature andhigh pressure, there is a case where a state where the condition is nota predetermined operation condition, for example, a state where therefrigerant piping in the refrigeration cycle circuit is blocked,blowing of the condenser is stopped, and the discharge pressure(high-pressure side of the refrigeration cycle circuit) excessivelyincreases due to forgetting of opening of two-way valve or three-wayvalve, or a state where the compression mechanism does not performcompression work of increasing the pressure of the refrigerant due toinsufficient torque of an electric motor (motor portion 3) of thecompressor, is generated.

Under the condition, when the power continues to be supplied to scrollcompressor 1200, a current is excessively supplied to the electric motorwhich configures scroll compressor 1200, and the electric motorgenerates heat. As a result, the electric motor in scroll compressor1200 is used as a heating element with respect to the refrigerant, andthe pressure and the temperature of the refrigerant in the insideincreases. As a result, an insulator of the winding wire whichconfigures a stator of the electric motor is dissolved, core wires(conducting wire) of the winding wire come into contact with each other,and a phenomenon which is called layer short-circuit occurs. Since highenergy is instantaneously transferred to the surrounding refrigerant,the layer short-circuit can become a starting point of adisproportionation reaction.

Here, in the embodiment, even in a case where the power continues to besupplied to the electric motor while the compression mechanism does notperform a pressure rise operation, an aspect in which the pressure riseof airtight container 201 which accommodates the electric motor, thatis, on the high-pressure side of the refrigeration cycle, is suppressed,and a condition of occurrence of a disproportionation reaction isavoided by the pressure, is achieved. Specifically, discharge chamber122 is configured to always communicate with compression chamber 215 inthe vicinity via discharge hole 218.

As described above, according to the embodiment, in a case where thepower continues to be supplied to the electric motor while thecompression mechanism does not perform the compression operation, theelectric motor heats the refrigerant in the inside of airtight container201 as a heating element. However, for example, even when the pressureof the refrigerant increases due to the heating, the pressure acts oncompression chamber 215 via discharge hole 218, it is possible torelease the pressure in the inside of airtight container 201 to thelow-pressure side of the refrigeration cycle circuit by reverselyrotating the compression mechanism, and therefore, it is possible toavoid an abnormal pressure rise which becomes a condition of occurrenceof a disproportionation reaction.

As described above, in a first aspect illustrated from the sixthembodiment to the tenth embodiment of the present invention, acompression chamber which is formed in both directions by meshing thefixed scroll and the revolving scroll in which a spiral lap from the endplate rises with each other by using a refrigerant containing1,1,2-trifluoroethylene as a working fluid, and by using the polyvinylether oil as a compressor lubricating oil, is provided. In addition, asuction volume of the first compression chamber formed on the lap outerwall side of the revolving scroll, is greater than a suction volume ofthe second compression chamber formed on the lap inner wall side of therevolving scroll.

According to this configuration, since it is possible to prevent therefrigerant from being heated in the path until reaching a confiningposition of first compression chamber 15 a, it is possible to suppress adisproportionation reaction of R1123. In addition, since the polyvinylether oil has a relatively low polarity, and it is easy to achieve aneffect of improving slidability by the additive, it is possible tosuppress local heat generation in the sliding portion, and to suppressself-degradable reaction of R1123.

In addition, in a second aspect, in the first aspect, the working fluidmay be a mixed working fluid containing difluoromethane, and a ratio ofdifluoromethane may be 30% by weight to 60% by weight. In addition, theworking fluid may be a mixed working fluid containing tetrafluoroethane,and a ratio of tetrafluoroethane may be 30% by weight to 60% by weight.In addition, the working fluid may be a mixed working fluid containingdifluoromethane and tetrafluoroethane, difluoromethane andtetrafluoroethane may be mixed, and proportions of difluoromethane andtetrafluoroethane may be 30% by weight to 60% by weight.

According to this, it is possible to suppress a disproportionationreaction of R1123, and to improve a refrigeration performance or COP.

In a third aspect, in the first or the second aspect, the polyvinylether oil may contain a phosphate ester anti-wear agent.

According to this, as the anti-wear agent is adsorbed to the frontsurface of the sliding portion and reduces wear, it is possible tosuppress heat generation, and to suppress self-degradable reaction ofthe refrigerant R1123.

In a fourth aspect, in any one aspect among the first or second aspect,the polyvinyl ether oil may contain the phenolic antioxidant.

According to this, since the phenolic antioxidant rapidly captures theradicals generated by the sliding portion, it is possible to prevent theradicals from reacting to the refrigerant R1123.

In a fifth aspect, in any one of the first to second aspects, thepolyvinyl ether oil may be lubricating oil which is obtained by mixing alubricating oil having a higher viscosity than that of the base oil witha terpene type or a terpenoid type of which an amount is equal to orgreater than 1% and less than 50%, or is obtained by mixing alubricating oil having a super-high viscosity of which an amount isequal to or greater than that of a terpene type or a terpenoid type inadvance therewith, and by mixing an oil additive of which the viscosityis adjusted to be viscosity equivalent to that of the base oil with thebase oil.

According to this, it is possible to suppress a disproportionationreaction of R1123.

In a sixth aspect, in the first or the second aspect, a motor portionmay use an electrical wire which is obtained by coating a conductor withthe thermosetting insulating material and baking with the insulatingfilm therebetween, as a coil.

According to this, by coating the winding wire of the coil for theelectric motor in the compressor with the thermosetting insulatingmaterial, while maintaining high resistance between the winding wireseven in a state where the coil infiltrates into the liquid refrigerant,it is possible to suppress the discharge, and as a result, to suppressdecomposition of the refrigerant R1123.

In a seventh aspect, in the first or the second aspect, an airtightcontainer may include a power supply terminal which is installed in amouth portion via the insulating member, and the connection terminal forconnecting the power supply terminal to a lead wire. In addition, thedoughnut-like insulating member which adheres to the insulating membermay be pipe-connected to the power supply terminal on an inner side ofthe airtight container.

According to this, since the insulating member is added to the powersupply terminal on the inner side of the metal housing, by extending theshortest distance between conductors, it is possible to suppress aninsulation defect of the power supply terminal, and to prevent ignitiondue to the discharge energy of R1123. In addition, it is possible toprevent a hydrogen fluoride generated when R1123 is decomposed fromcoming into contact with a glass insulating material, and to prevent theglass insulating material from corroding and being damaged.

In an eighth aspect, in the first to seventh aspects, the refrigerationcycle device is a refrigeration cycle device, in which the compressor ofany one of aspects; the condenser which cools a refrigerant gas that iscompressed by the compressor and has a high pressure; the throttlemechanism which reduces the pressure of the high-pressure refrigerantwhich is liquefied by the condenser; and the evaporator which gasifiesthe refrigerant of which the pressure is reduced by the throttlemechanism, are linked to each other by the piping.

According to this, it is possible to suppress a disproportionationreaction of R1123, to improve a refrigeration performance and COP.

In a ninth aspect, in the eighth aspect, the condensation temperaturedetecting portion provided in the condenser may be provided, and adifference between the critical temperature of the working fluid and thecondensation temperature detected by the condensation temperaturedetecting portion may control the opening degree of the throttlemechanism to become equal to or greater than 5K.

According to this, by making the working fluid temperature measured bythe temperature detecting portion correspond to the pressure, it ispossible to suppress the opening degree of the throttle mechanism tolimit the working fluid temperature (pressure) on a high-pressure sideto be equal to or greater than 5K considering a margin of safety fromthe critical pressure. Accordingly, since it is possible to prevent thehigher condensation pressure from excessively increasing, as a result(result in which the distance by which the molecules approach eachother), it is possible to suppress a disproportionation reaction whichsuppresses a disproportionation reaction which is a concern to begenerated, and to ensure the reliability of the device.

In a tenth aspect, in the eighth aspect, the high-pressure side pressuredetecting portion provided between the discharge portion of thecompressor and the inlet of the throttle mechanism, may be provided, andthe difference between the critical pressure of the working fluid andthe pressure detected by the high-pressure side pressure detectingportion may control the opening degree of the throttle mechanism to beequal to or greater than 0.4 MPa.

According to this, regarding the working fluid containing R1123, inparticular, in a case where a zeotropic refrigerant having a largetemperature gradient is used, it is possible to more accurately detectthe pressure of the refrigerant, and further, to decrease the pressure(condensation pressure) on the high-pressure side in the refrigerationcycle device by performing the control of the opening degree of thethrottle mechanism by using the detection result. Accordingly, it ispossible to suppress a disproportionation reaction, and to improve thereliability of the device.

In an eleventh aspect, in the eighth aspect, the condenser outlettemperature detecting portion provided between the condenser and thethrottle mechanism may be provided, and may control the opening degreeof the throttle mechanism so that the difference between thecondensation temperature detected by the condensation temperaturedetecting portion and the condenser output temperature detected by thecondenser outlet temperature detecting portion is equal to or less than15K.

According to this, by using the detection result of the overcoolingdegree illustrated by the difference between the condensationtemperature detecting portion and the condenser outlet temperaturedetecting portion, it is possible to perform the control of the openingdegree of the throttle mechanism, and to prevent the pressure of theworking fluid in the inside of the refrigeration cycle device fromexcessively increasing. Accordingly, it is possible to suppress adisproportionation reaction, and to improve the reliability of thedevice.

In a twelfth aspect, in the eighth aspect, the first transportingportion which transports the first medium that exchanges the heat in thecondenser, a second transporting portion which transports the secondmedium that exchanges the heat in the evaporator, the condensationtemperature detecting portion which is provided in the condenser, thefirst medium temperature detecting portion which detects the temperatureof the first medium before flowing into the condenser, and the secondmedium temperature detecting portion which detects the temperature ofthe second medium before flowing into the evaporator, are provided. Inaddition, a case where at least any one of the amount of change per unittime of the input of the compressor, the amount of change per unit timeof the input of the first transporting portion, and the amount of changeper unit time of the input of the second transporting portion, issmaller than a predetermined value determined in advance. In addition,in a case where the amount of change per unit time of the temperature ofthe first medium detected by the first medium temperature detectingportion is greater than any one of the amount of change per unit time ofthe condensation temperature detected by the condensation temperaturedetecting portion, and the amount of change per unit time of thetemperature of the second medium detected by the second mediumtemperature detecting portion, the throttle mechanism may be controlledin the opening direction.

According to this, in a case where an aspect of the surrounding mediumdoes not change, in a case where the condensation temperature rapidlychanges, since it is considered that the pressure increases due to adisproportionation reaction, it is possible to control the openingdegree of the throttle mechanism to be high. Accordingly, it is possibleto improve the reliability of the device.

In a thirteenth aspect, in any one of the eighth to twelfth aspects, theouter circumference of the joint of the piping which configures therefrigeration cycle circuit may be covered with a sealing compoundcontaining the polymerization promoter.

According to this, in a case where the working fluid leaks from thejoint, the polymerization product is generated as polymerizationreaction is performed with respect to the polymerization promotercontained in the sealing compound and the working fluid containingR1123. Accordingly, the leakage is likely to be visually confirmed, thepolymerization product acts to prevent the flow of the refrigerantemitted to the outside, and it is possible to control the leakage of therefrigerant.

In a fourteenth aspect, in any one of the first to seventh aspects, thedischarge chamber may always communicate with the compression chambervia the discharge hole.

According to this, the power is supplied to the electric motor while thecompression mechanism does not perform the compression operation, theelectric motor heats the refrigerant in the inside of the airtightcontainer as the heat element, and even when the pressure of therefrigerant increases, the pressure acts on the compression chamber viathe discharge hole, and the pressure in the inside of the airtightcontainer is released to the low-pressure side of the refrigerationcycle circuit by reversely rotating the compression mechanism.Therefore, it is possible to avoid the abnormal pressure rise whichbecomes a condition of occurrence of a disproportionation reaction.

INDUSTRIAL APPLICABILITY

As described above, the present invention is effective since it ispossible to provide a compressor, lubricating oil, and a refrigerationcycle device which are more appropriate than using the working fluidcontaining R1123, and thus, it is also possible to be employed in use ofa water heater, a car air conditioner, a refrigerator-freezer, and adehumidifier.

REFERENCE MARKS IN THE DRAWINGS

-   1 AIRTIGHT CONTAINER-   2 COMPRESSION MECHANISM PORTION-   3 MOTOR PORTION-   4 SHAFT-   4 a ECCENTRIC SHAFT PORTION-   6 COMPRESSOR LUBRICATING OIL-   11 MAIN BEARING MEMBER-   12 FIXED SCROLL-   13 REVOLVING SCROLL-   13 c REVOLVING SCROLL LAP-   13 e REAR SURFACE-   14 ROTATION RESTRAINING MECHANISM-   15 COMPRESSION CHAMBER-   15 a, 15 a-1, 15 a-2 FIRST COMPRESSION CHAMBER-   15 b, 15 b-1, 15 b-2 SECOND COMPRESSION CHAMBER-   16 SUCTION PIPE-   17 SUCTION PORT-   18 DISCHARGE HOLE-   19 REED VALVE-   20 OIL STORAGE PORTION-   25 PUMP-   26 OIL SUPPLY HOLE-   29 BACKPRESSURE CHAMBER-   30 HIGH-PRESSURE REGION-   31 DISCHARGE CHAMBER-   32 MUFFLER-   50 DISCHARGE PIPE-   61 COMPRESSOR-   62 CONDENSER-   63 THROTTLE MECHANISM-   64 EVAPORATOR-   66 BEARING PORTION-   68, 68 a-1, 68 a-2, 68 b-1, 68 b-2, 68 ab-1, 68 ab-2, 68 ab-3 BYPASS    HOLE-   69 VALVE STOP-   71 POWER SUPPLY TERMINAL-   72 GLASS INSULATING MATERIAL-   73 METAL LID BODY-   74 FLAG TERMINAL-   75 LEAD WIRE-   76 INSULATING MEMBER-   78 SEAL MEMBER-   100, 101, 130, 140 REFRIGERATION CYCLE DEVICE-   102 COMPRESSOR-   103 CONDENSER-   104 EXPANSION VALVE-   105 EVAPORATOR-   106 REFRIGERANT PIPING-   107 a,107 b FLUID MACHINERY-   108 ISOTHERM-   109 SATURATION LIQUID LINE AND SATURATION VAPOR LINE-   110 a CONDENSATION TEMPERATURE DETECTING PORTION-   110 b CONDENSER OUTLET TEMPERATURE DETECTING PORTION-   110 c EVAPORATION TEMPERATURE DETECTING PORTION-   110 d SUCTION TEMPERATURE DETECTING PORTION-   110 e FIRST MEDIUM TEMPERATURE DETECTING PORTION-   110 f SECOND MEDIUM TEMPERATURE DETECTING PORTION-   111 UNION FLARE-   112 SEAL-   113 BYPASS PIPE-   114 RELIEF VALVE-   115 a HIGH-PRESSURE SIDE PRESSURE DETECTING PORTION-   115 b LOW-PRESSURE SIDE PRESSURE DETECTING PORTION-   116 FLOW PATH OF SURROUNDING MEDIUM-   117 PIPING JOINT-   120 OIL STORAGE PORTION-   121 VALVE STOP-   122 DISCHARGE CHAMBER-   123 DISCHARGE PIPE-   124 MUFFLER-   125 PUMP-   126 OIL SUPPLY HOLE-   129 BACKPRESSURE CHAMBER-   161 COMPRESSOR-   162 CONDENSER-   163 THROTTLE MECHANISM-   164 EVAPORATOR-   166 BEARING PORTION-   168, 168 a-1, 168 a-2, 168 b-1, 168 b-2, 168 ab-1, 168 ab-2, 168    ab-3 BYPASS HOLE-   171 POWER SUPPLY TERMINAL-   172 GLASS INSULATING MATERIAL-   173 METAL LID BODY-   174 FLAG TERMINAL-   175 LEAD WIRE-   176 INSULATING MEMBER-   178 SEAL MEMBER-   200 SCROLL COMPRESSOR-   201 AIRTIGHT CONTAINER-   202 COMPRESSION MECHANISM PORTION-   203 MOTOR PORTION-   204 SHAFT-   204 a ECCENTRIC SHAFT PORTION-   206 COMPRESSOR LUBRICATING OIL-   211 MAIN BEARING MEMBER-   212 FIXED SCROLL-   213 REVOLVING SCROLL-   213 e REAR SURFACE-   214 ROTATION RESTRAINING MECHANISM-   215 COMPRESSION CHAMBER-   215 a FIRST COMPRESSION CHAMBER-   215 b SECOND COMPRESSION CHAMBER-   216 SUCTION PIPE-   217 SUCTION PORT-   218 DISCHARGE HOLE-   219 REED VALVE-   230 HIGH-PRESSURE REGION-   1100, 1101, 1130, 1140 REFRIGERATION CYCLE DEVICE-   1102 COMPRESSOR-   1103 CONDENSER-   1104 EXPANSION VALVE-   1105 EVAPORATOR-   1106 REFRIGERANT PIPING-   1107 a, 1107 b FLUID MACHINERY-   1108 ISOTHERM-   1109 SATURATION LIQUID LINE AND SATURATION VAPOR LINE-   1110 a CONDENSATION TEMPERATURE DETECTING PORTION-   1110 b CONDENSER OUTLET TEMPERATURE DETECTING PORTION-   1110 c EVAPORATION TEMPERATURE DETECTING PORTION-   1110 d SUCTION TEMPERATURE DETECTING PORTION-   1110 e FIRST MEDIUM TEMPERATURE DETECTING PORTION-   1110 f SECOND MEDIUM TEMPERATURE DETECTING PORTION-   1111 UNION FLARE-   1112 SEAL-   1113 BYPASS PIPE-   1114 RELIEF VALVE-   1115 a HIGH-PRESSURE SIDE PRESSURE DETECTING PORTION-   1115 b LOW-PRESSURE SIDE PRESSURE DETECTING PORTION-   1116 FLOW PATH OF SURROUNDING MEDIUM-   1117 PIPING JOINT-   1200 SCROLL COMPRESSOR

1. A compressor which uses a refrigerant containing1,1,2-trifluoroethylene as a working fluid, and uses a polyvinyl etheroil as a compressor lubricating oil, comprising: a fixed scroll and arevolving scroll each having a spiral lap rising from an end plate; acompression chamber which is formed by meshing the fixed scroll and therevolving scroll; a discharge hole which is provided at a centerposition of the end plate of the fixed scroll, and is open to adischarge chamber; a bypass hole which is provided in the end plate ofthe fixed scroll, and communicates with the compression chamber and thedischarge chamber at a timing different from a timing at which thecompression chamber communicates with the discharge hole; and a checkvalve which is provided in the bypass hole, and allows a flow from acompression chamber side to a discharge chamber side.
 2. The compressorof claim 1, wherein the check valve is a reed valve provided on an endplate surface of the fixed scroll.
 3. The compressor of claim 1, whereinthe discharge chamber always communicates with the compression chambervia the discharge hole.
 4. A compressor which uses a refrigerantcontaining 1,1,2-trifluoroethylene as a working fluid, and uses apolyvinyl ether oil as a compressor lubricating oil, comprising: a fixedscroll and a revolving scroll each having a spiral lap rises from an endplate; a compression chamber which is formed by engaging the fixedscroll and the revolving scroll; a first compression chamber which isformed on an outer wall side of the lap of the revolving scroll; and asecond compression chamber which is formed on an inner wall side of thelap of the revolving scroll, wherein a suction volume of the firstcompression chamber is greater than a suction volume of the secondcompression chamber.
 5. The compressor of claim 4, wherein a dischargechamber is provided in the end plate of the fixed scroll, and thedischarge chamber always communicates with the compression chamber via adischarge hole.
 6. The compressor of claim 1, wherein the working fluidis any one of configurations of a mixed working fluid containingdifluoromethane in which there is at least 30% by weight to at most 60%by weight of difluoromethane, a mixed working fluid containingtetrafluoroethane in which there is at least 30% by weight to at most60% by weight of tetrafluoroethane, and a mixed working fluid containingdifluoromethane and tetrafluoroethane in which the difluoromethane andthe tetrafluoroethane are mixed with each other, and in whichproportions at which the difluoromethane and the tetrafluoroethane areincorporated with each other is at least 30% by weight to at most 60% byweight.
 7. The compressor of claim 1, wherein the polyvinyl ether oilcontains a phosphate ester anti-wear agent.
 8. The compressor of claim1, wherein the polyvinyl ether oil contains a phenolic antioxidant. 9.The compressor of claim 1, wherein the polyvinyl ether oil is alubricating oil which is obtained by mixing a lubricating oil having ahigher viscosity than a viscosity of a base oil with a terpene type or aterpenoid type of which an amount is equal to or greater than 1% andless than 50%, or is obtained by mixing a lubricating oil having asuper-high viscosity of which an amount is equal to or greater than anamount of a terpene type or a terpenoid type in advance therewith, andby mixing an oil additive of which the viscosity is adjusted to beequivalent to the viscosity of the base oil with the base oil.
 10. Thecompressor of claim 1, further comprising: a motor portion which drivesthe revolving scroll, wherein the motor portion uses an electrical wirewhich is obtained by coating a conductor with a thermosetting insulatingmaterial and baking with an insulating layer therebetween, as a coil.11. The compressor of claim 1, further comprising: an airtight containerwhich accommodates the compression chamber and the motor portion,wherein the airtight container includes a power supply terminal which isinstalled in a mouth portion via an insulating member, a connectionterminal for connecting the power supply terminal to a lead wire, and adoughnut-like insulating member which is disposed to adhere to theinsulating member on the power supply terminal on an inner side of theairtight container.
 12. A refrigeration cycle device comprising: thecompressor of claim 1; a condenser which cools a refrigerant gas that iscompressed by the compressor and has a high pressure; a throttlemechanism which reduces a pressure of a high-pressure refrigerant whichis liquefied by the condenser; an evaporator which gasifies therefrigerant of which the pressure is reduced by the throttle mechanism;and piping which links the compressor, the condenser, the throttlemechanism, and the evaporator to each other.
 13. The compressor of claim2, wherein the discharge chamber always communicates with thecompression chamber via the discharge hole.
 14. The compressor of claim4, wherein the working fluid is any one of configurations of a mixedworking fluid containing difluoromethane in which there is at least 30%by weight to at most 60% by weight of difluoromethane, a mixed workingfluid containing tetrafluoroethane in which there is at least 30% byweight to at most 60% by weight of tetrafluoroethane, and a mixedworking fluid containing difluoromethane and tetrafluoroethane in whichthe difluoromethane and the tetrafluoroethane are mixed with each other,and in which proportions at which the difluoromethane and thetetrafluoroethane are incorporated with each other is at least 30% byweight to at most 60% by weight.
 15. The compressor of claim 4, whereinthe polyvinyl ether oil contains a phosphate ester anti-wear agent. 16.The compressor of claim 4, wherein the polyvinyl ether oil contains aphenolic antioxidant.
 17. The compressor of claim 4, wherein thepolyvinyl ether oil is a lubricating oil which is obtained by mixing alubricating oil having a higher viscosity than a viscosity of a base oilwith a terpene type or a terpenoid type of which an amount is equal toor greater than 1% and less than 50%, or is obtained by mixing alubricating oil having a super-high viscosity of which an amount isequal to or greater than an amount of a terpene type or a terpenoid typein advance therewith, and by mixing an oil additive of which theviscosity is adjusted to be equivalent to the viscosity of the base oilwith the base oil.
 18. The compressor of claim 4, further comprising: amotor portion which drives the revolving scroll, wherein the motorportion uses an electrical wire which is obtained by coating a conductorwith a thermosetting insulating material and baking with an insulatinglayer therebetween, as a coil.
 19. The compressor of claim 4, furthercomprising: an airtight container which accommodates the compressionchamber and the motor portion, wherein the airtight container includes apower supply terminal which is installed in a mouth portion via aninsulating member, a connection terminal for connecting the power supplyterminal to a lead wire, and a doughnut-like insulating member which isdisposed to adhere to the insulating member on the power supply terminalon an inner side of the airtight container.
 20. A refrigeration cycledevice comprising: the compressor of claim 4; a condenser which cools arefrigerant gas that is compressed by the compressor and has a highpressure; a throttle mechanism which reduces a pressure of ahigh-pressure refrigerant which is liquefied by the condenser; anevaporator which gasifies the refrigerant of which the pressure isreduced by the throttle mechanism; and piping which links thecompressor, the condenser, the throttle mechanism, and the evaporator toeach other.